Buffer valve

ABSTRACT

A buffer valve is installed on a pneumatic diaphragm valve. An inner flow channel of the buffer valve includes an inner micro gas hole, an inner chamber, an outer gas hole, and a floating ball. The buffer valve has functions with a high-filling action, a shielding action, a releasing action, a shielding time Δt, and an adjusting mechanism. When inflatable, the floating ball will not block the inner micro hole to be quickly filled with high-pressure gas. when gas discharge, the floating ball will move to the outer gas hole with the gas flow and produce the shielding action to reduce the discharge rate to reduce the vibration and slow down the approach speed of the diaphragm to reduce the impact against the valve seat. When the pressure of the gas decreases, the floating ball is separated from the outer gas hole by the releasing action to accelerate the discharge.

CROSS-REFERENCE TO RELATED APPLICATIONS

This patent application is a continuation in part of U.S. patentapplication Ser. No. 17/812,045, filed on Apr. 27, 2022.

FIELD OF THE INVENTION

The present invention relates to a buffer valve, and more particularlyto a buffer valve that is a two-way valve installed on a breathing holeof a pneumatic diaphragm valve for conveying high cleanliness fluid. Thepneumatic diaphragm valve has a diaphragm and a valve seat. The buffervalve can slow down the opening and closing action of the pneumaticdiaphragm valve, so as to reduce the impact of a central portion of thediaphragm against the valve seat and the vibration generated by therapid release of a high-pressure gas. Such impact and vibration willincrease the separation of the material and cause pollution. In recentyears, the further pursuit of wafer grinding is that the suspendedparticles of the conveying fluid will not produce an impinging jet flowdue to the closing of the central portion and the valve seat. The rapidrelease of the high-pressure gas causes the trajectory of suspendedparticles to be away from the direction of the fluid, resulting incollisions and condensation.

BACKGROUND OF THE INVENTION

A conventional pneumatic diaphragm valve includes a pneumatic cylinder,a diaphragm, and a valve seat. The pneumatic cylinder is divided into apneumatic chamber and a spring chamber by a piston. The spring chamberis provided with a spring. The spring chamber and the pneumatic chambereach have a breathing hole. The breathing hole of the pneumatic chamberis used for filling a high-pressure gas, and the gas pressure usuallyranges from 3 bar to 7 bar. The conventional diaphragm is an integralstructure, having a peripheral portion, a central portion and an elasticportion. The cross-sectional shape of the elastic portion is like aΩ-shaped curve having a longer curve length. The arc-shaped curvesurrounds an axis to form an annular curve structure with an axis hole.The outer circumference of the elastic portion is connected to theperipheral portion. The periphery of the center is connected to thecentral portion. The arc-shaped curve has more extension space but alower tensile ratio. When the central portion is displaced, thearc-shaped curve provides more deformation and extension, so that thecentral portion has more and faster displacement, and its lower tensileratio brings longer service life of the diaphragm. The movement of thecentral portion will pull the elastic portion with a smaller diameter tomove, so that the elastic portion can bear less fluid pressure withoutreducing the leaving speed of the central portion. In another structureof the diaphragm, its elastic portion is a concave spherical structurein the shape of a pot lid, having a shorter curve length and a highertensile ratio. The curve provides a larger area of deformation andextension to maintain the displacement of the central portion when thecentral portion is displaced, and its higher tensile ratio brings aslightly shorter service life of the diaphragm. The pneumatic diaphragmvalve is classified into a normally closed valve and a normally openvalve. The normally closed valve is forced by the elastic force of thespring in the spring chamber so that the central portion is in closecontact with the valve seat to keep closed. Taking a 1-inch valve as anexample, the pressing force of the spring is 70 kg. The normally openvalve is supported by the elastic force of the spring in the springchamber, so that the central portion is separated from the valve seat tokeep open. Taking a 1-inch valve as an example, the tension of thespring is 30 kg. The pneumatic chamber of the normally closed valve islocated on the rear side of the diaphragm. The spring chamber of thenormally open valve is located on the rear side of the diaphragm. Thepneumatic chamber is used for filling a high-pressure gas to push thepiston to compress the spring. When the normally closed valve is opened,the central portion has a leaving speed relative to the valve seat. Whenthe normally open valve is closed, the central portion has an approachspeed relative to the valve seat. When these two valves perform suchactions, the more compressed the spring in the spring chamber, thehigher the rebound force. Such a rebound force provides a good bufferingeffect, and there will not be too much impact. The pneumatic chamber issubjected to a gradually rising pressure to reduce the vibration of thehigh-pressure gas. At the moment of filling the high-pressure gas, thepiston will not move quickly. When the central portion moves away fromthe valve seat, only a slight negative vacuum is generated. When thehigh-pressure gas is released, the pressure of the pneumatic chamberdrops sharply. There will be vibrations released by the high-pressuregas. In general, the pressure of the exhaust pipe is the atmosphere, andthe absolute pressure is 1 bar. Compression ratio of absolutepressure=pressure of high-pressure gas/pressure of the exhaust pipe.When the compression ratio released by the high-pressure gas is >1.5times, the violent vibration of the ultrasonic wave will be generated.The spring also releases its compressed rebound force to push the pistontoo fast. For the normally closed valve, the central portion approachesthe valve seat fast to impact the valve seat. For the normally openvalve, the central portion leaves the valve seat fast to create a briefnegative vacuum at the valve seat. For the normally closed valve, thecentral portion will impact the valve seat at a high approach speedduring the process of gas discharge, and the arc-shaped curve of theelastic portion cannot obtain a buffering effect from the fluidpressure. In such a closing process, there is jet flow produced by thewater hammer effect. This water hammer effect not only produces jet flowbut also transmits pressure waves up and down the pipeline, which willcause damage to other equipment or joints on the pipeline or release ofunwanted particles to contaminate clean fluids. For the normally openvalve, the central portion will move away from the valve seat at a highspeed during the process of gas discharge, and the arc-shaped curve ofthe elastic portion will move up sharply. The delivery fluid cannot bereplenished in a short time, resulting in a short-term negative pressureeffect near the valve seat, which causes the fluid in the diaphragm toproduce short-term intense turbulent flow and eddy flow. These fluidsproduce violent phenomena when the valve is opened and closed. Insemiconductor process, in addition to the impact of the center portionagainst the valve seat to generate material particles, the jet flow,turbulent flow and eddy flow also release undesired particles along thepipeline and damage the pipeline and equipment. Liquids containingsuspended particles may cause particles to move in directions that areinconsistent with the direction of the fluid, resulting in the problemof particle agglutination due to static electricity generated fromcollisions.

From the above description, the basic application requirements of thepneumatic diaphragm valve for delivering high cleanliness fluids can beclassified into the following two problems:

-   -   First Problem: The fluid to be conveyed will not be affected        because the central portion is moved toward the valve seat too        fast, resulting in the problem of the jet flow produced by water        hammer and the problem of the vibration of the pressure wave        transmitted to the pipeline upstream and downstream, or the        central portion is moved away from the valve seat too fast,        resulting in the problem of transient severe turbulent flow and        eddy flow.    -   Second Problem: When the high-pressure gas is discharged through        the pneumatic chamber of the diaphragm valve, there will be no        violent vibration and no shock wave transmitted to the liquid        conveying pipe upstream and downstream.

If these two problems can be solved at the same time, the followingfirst, second and third requirements can be met at the same time becauseeach problem involves needs the first, second and third requirements.

-   -   First Requirement: reducing particles being released.    -   Second Requirement: reducing the damage to the joints and        devices on the pipeline, especially reducing the risk of        leakage.    -   Third Requirement: reducing the condensation of suspended        particles.    -   Fourth Requirement: adjusting the opening and closing time of        the diaphragm valve.

The third requirement is a new requirement in response to the latestsemiconductor process requirements. The fourth requirement is to providemore adjustment requirements for the length of the operation time indifferent processes when solving the first and second problems.

In the prior art, several references solutions have been proposed forthe first and second problems. These reference solutions also hope tomeet the first, second, third and fourth requirements. The following arethe reference solutions of the prior art.

First Reference

U.S. Pat. No. 5,779,224A titled “poppet valve” published in 1998 aims ata solution to the first problem, hoping to solve the problem of theimpact of the central portion against the valve seat. The solution tothe problem is to provide a rubber cushion the rear side of thediaphragm. The rubber cushion just protects the diaphragm itself, anddoes not solve the violent vibration caused by the release of thehigh-pressure gas that is not slowed down when released. It is unable tosolve the second problem. An auxiliary spring with a low elastic forceis installed in the pneumatic chamber of the normally closed diaphragmvalve, so that the diaphragm can be buffered and closed smoothly when itis closed. This can reduce the impact of the central portion against thevalve seat greatly and generate less vibration and release fewerparticles, but it does not mention how much the approach speed isreduced by reducing the impact. That is, it is possible that the firstproblem is not completely solved, and it is impossible to confirm thatthe problem of the jet flow of the fluid is solved.

Second Reference

U.S. Pat. No. 5,865,423A titled “high flow diaphragm valve” published in1999 aims at a solution to the first problem. The solution to theproblem of jet flow produced by water hammer is proposed. A valvechamber surrounding the valve seat is in the shape of a bowl, and theelastic portion of the matched diaphragm is shaped like a pot lid. Thelength of the curve of the section is shorter than that of the structurewith a Ω-shaped section. The movement of the central portion will pullthe elastic portion with a larger diameter area to move. In practice,the valve chamber has a larger outer diameter so that the diaphragm alsohas a larger diameter to withstand the deformation. In this way, theelastic portion with a larger diameter area can withstand more fluidpressure. When the central portion moves toward the valve seat, thediaphragm will have a relatively large area to withstand the fluidpressure to reduce its approach speed, and the bowl-shaped valve chambercan obtain a larger flow rate when it is opened. U.S. Pat. No.6,123,320A titled “sanitary diaphragm valve” published in 2000 also hasa similar bowl-shaped valve chamber structure. The elastic portion ofthe diaphragm is also shaped like a pot lid. However, in the test, theapproach speed was not significantly reduced and the vibration caused bythe release of the high-pressure gas was not significantly reduced, thatis, the first problem was not completely solved. The problem of j etflow of the fluid cannot be solved. Secondly, the problem of vibrationreleased by the high-pressure gas has not been solved.

Third Reference

Japanese Patent No. JPH09217845 (A) titled “diaphragm Valve” publishedin 1999 aims at a solution to the first problem. An auxiliary springwith a lower elastic value is installed in the pneumatic chamber of thenormally closed diaphragm valve. The normally closed spring above thepiston ensures that the diaphragm can be pressed against the valve seat.The auxiliary spring under the piston allows the diaphragm to bebuffered and closed smoothly. This can reduce the impact of the centralportion against the valve seat greatly and generate less vibration andrelease fewer particles, but it does not mention how much the approachspeed is reduced by reducing the impact. That is, it is possible thatthe first problem is not completely solved, and it is impossible toconfirm that the problem of the jet flow of the fluid is solved.Secondly, it does not solve the second problem. When the high-pressuregas is released, it will still not be slowed down and will produceviolent vibrations.

Fourth Reference

Japanese Patent No. JP2009180338(A) titled “fluid control valve andoperation air intermediate valve” published in 2009 introduces aminiature valve mechanism to further improve the problem. The miniaturevalve mechanism has a micro gas hole, a miniature piston, a miniaturespring, a miniature sealing surface and a miniature fixing seat. Theminiature piston has a miniature flange on the open side of theminiature fixing seat. The miniature spring is mounted on the outersurface of the miniature piston, and is restricted to the inner side ofthe miniature fixing seat by the miniature flange. Part of the miniaturepiston is exposed to the outlet of the miniature fixing seat. Theminiature piston can be sealed with the miniature sealing surface. Theminiature sealing surface is installed on the inner side of thebreathing hole in the pneumatic chamber. The miniature gas hole isdisposed on the miniature piston, enabling the miniature piston tocommunicate with the exterior space of the miniature fixing seat. Theminiature fixing seat has a through hole communicating with thepneumatic chamber.

In the first embodiment, the miniature fixing seat is installed on thepiston and is located on one side of the pneumatic chamber and can moveup and down along with the piston. When the piston is at the positionwhere the valve is opened, the miniature valve mechanism moves alongwith the piston to the position where the valve is opened and does notcover the breathing hole, and the open surface of the fixing seat is incontact with the inner surface of the pneumatic chamber located at theside of the valve seat, and the miniature piston completely seals theminiature sealing surface and the breathing hole. When the piston is atthe position where the valve is closed, the breathing hole is to befilled with a high-pressure gas to open the valve. At this time, thehigh-pressure gas first passes through the micro gas hole of theminiature piston and is restricted in the gas flow. As the pressure ofthe pneumatic chamber gradually increases, the piston moves toward thespring chamber and compresses the spring. At this time, the miniaturevalve mechanism also moves and allows the breathing hole to acceleratethe filling of the gas. When the valve is at the open position, thepneumatic chamber is completely filled with the high-pressure gas, andthe piston fully compresses the spring of the spring chamber. When thevalve is switched to be closed, the miniature valve mechanism willgradually cover the breathing hole when it is close to the miniaturesealing surface until the breathing hole is completely covered. Atfirst, the release of the high-pressure gas is not affected by theminiature mechanism until the breathing hole is gradually covered, theminiature gas hole will restrict the flow of the released residualhigh-pressure gas.

In the second embodiment, the miniature valve mechanism is installedinside the breathing hole of the pneumatic chamber and is driven by theopening and closing actions of the valve. When the piston is at theposition where the valve is opened, the miniature spring of theminiature valve mechanism lifts the miniature piston without coveringthe breathing hole. When the valve is switched to be closed, thehigh-pressure gas will first flow through the ventilation hole to enterthe fixing seat and then to enter the breathing hole. At this time, thegas flow is released in an unrestricted manner. When the central portionis close to the valve seat, the surface of the piston will contact andpress the miniature piston to move until it contacts and seals thesealing surface. At this time, the gas flow is released in a restrictedmanner.

In the above two embodiments, first, the piston moves at a normal speedand an accelerated speed. When the breathing hole is gradually covered,the piston is no longer accelerated but gradually decelerated. But, theelastic force of the spring continues to act plus the momentum of thepiston. At the position where the valve is closed, the central portionof the diaphragm still impacts the valve seat. This still does not solvethe first problem, namely, the problem of water hammer and jet flowbetween the central portion and the valve seat. When the pneumaticchamber releases the high-pressure gas at the initial stage, thehigh-pressure gas will directly flow out of the breathing hole. At thistime, there will be violent vibration from the release of the gas. Untilthe breathing hole is gradually covered, it no longer produces violentvibration. Such a high-pressure gas release process still does not solvethe second problem, namely, the problem of violent vibration caused bythe high-pressure gas. The miniature valve mechanism is linked with theopening and closing mechanism and lacks room for adjustment andimprovement of the stroke. Basically, it cannot meet the fourthrequirement. The opening and closing time of the diaphragm valve mustmeet the requirements.

Fifth Reference

Taiwanese Patent No. TW202010966A titled “diaphragm valve structure”published in 2020 aims at a solution to the first problem and the secondproblem. This diaphragm valve structure is applied to diaphragm valvesmade of perfluoro resin at 200° C. Regarding the non-particle releasestructure, it is mentioned that the piston includes an annular portion,a lower annular rib, an upper annular rib, and a damping ring. The uppervalve body is mounted on the inner side of the annular portion, and hasan open cup-shaped structure with a central conical protrusion, andincludes an outer annular surface, a pressing portion, a shaft holeportion, a first annular groove, a second annular groove, and adiaphragm chamber. The damping ring is coupled with the first annulargroove. The damping ring is in sliding fit with the first annulargroove. When the diaphragm moves up and down, it can provide a dampingeffect to absorb shock. The lower annular rib is coupled with the secondannular groove. The lower annular rib is in sliding fit with the secondannular groove. When the diaphragm moves up and down, it can provide adamping effect to absorb shock. This is to slow down the release of thegas to achieve shock absorption. However, because the method is achievedthrough structural conditions, it is impossible to further adjust theconditions for shock absorption according to the demand. It isimpossible to meet the fourth requirement. The opening and closing timeof the diaphragm valve must meet the requirements, and variation instructural and dimensional tolerances may affect the control ofreleasing the gas.

Sixth Reference

Taiwanese Patent No. TW202045845 titled “fluid control valve” publishedin 2020 aims at a solution to the first problem and the second problem.The method of this reference is similar to that of the fourth referencebut slightly different. The fluid control valve has a pneumaticcylinder, and the pneumatic cylinder is divided into a pneumatic chamberand a spring chamber by a piston. The spring chamber is provided with aspring. The spring chamber and the pneumatic chamber each have abreathing hole. The breathing hole of the pneumatic chamber is used forfilling a high-pressure gas. When the piston is at the position wherethe valve is opened, the fluid is received in the pneumatic chamber. Thefluid is discharged through the breathing orifice as the piston isdisplaced toward the position where the valve is closed.

In the first embodiment, a throttling portion is disposed on one side ofthe pneumatic chamber and can move up and down along with the piston.The throttling portion may be an annular structure. A throttling flowpath with a flow path cross-sectional area less than that of thebreathing hole is formed between the throttling portion and the innerwall of the pneumatic pressure, or a flow restricting portion has a flowrestricting slit. When the piston is at the position where the valve isopened, the throttling portion does not cover the breathing hole. Whenthe piston is at the position where the valve is closed, the throttlingportion completely covers the breathing hole. When the piston is at theposition where the valve is closed, the breathing hole is to be filledwith a high-pressure gas to open the valve. At this time, thehigh-pressure gas first passes through the restricting flow channel andis restricted in the gas flow. As the pressure of the pneumatic chambergradually increases, the piston moves toward the spring chamber andcompresses the spring. At this time, the restricting flow channel alsomoves to expose the breathing hole with a larger cross-sectional area ofthe flow path to accelerate the filling of the gas. When the valve is atthe open position, the pneumatic chamber is completely filled with thehigh-pressure gas, and the piston fully compresses the spring of thespring chamber. When the valve is switched to be closed, the throttlingportion will gradually cover the breathing hole until it is completelycovered. At first, the release of the high-pressure gas is not affectedby the flow restricting portion until the breathing hole is graduallycovered, the flow restricting portion will restrict the flow of thereleased high-pressure gas. That is, the piston moves at a normal speedand an accelerated speed. When the breathing hole is gradually covered,the piston is no longer accelerated but gradually decelerated. But, theelastic force of the spring continues to act plus the momentum of thepiston. At the position where the valve is closed, the central portionof the diaphragm still impacts the valve seat. This still does not solvethe first problem, namely, the problem of water hammer and jet flowbetween the central portion and the valve seat. When the pneumaticchamber releases the high-pressure gas at the initial stage, thehigh-pressure gas will first flow through the breathing hole that is notcovered by the flow restricting slit. At this time, there will beviolent vibration from the release of the gas. Until the breathing holeis gradually covered by the flow restricting portion, it no longerproduces violent vibration. Such a high-pressure gas release processstill does not solve the second problem, namely, the problem of violentvibration caused by the high-pressure gas. Both the flow restrictingslit and the restricting flow channel are formed through a gap or slitin a fixed structure, which lacks room for adjustment and improvement.Basically, it cannot meet the fourth requirement. The opening andclosing time of the diaphragm valve must meet the requirements. Thethrottling portion of the first embodiment may be applied to a normallyopen valve. The throttling portion is disposed in the spring chamber.When the pneumatic chamber is filled with the high-pressure gas, the gasin the spring chamber is restricted to flow out slowly, so that thecentral portion of the diaphragm approaches the valve seat at a lowspeed. However, because the pressure of the spring chamber is only oneatmosphere, scarce air quality is not easy to have a good result. Ingeneral, the buffering effect of the pneumatic chamber filled with thehigh-pressure gas is still borne by the spring. Secondly, when thehigh-pressure gas in the pneumatic chamber is released to open thevalve, the vibration generated by the rapid release of the high-pressuregas cannot solve the second problem. The spring pushes the piston sothat the central portion is removed at a high speed, resulting inshort-term negative pressure, turbulent flow and eddy flow near thevalve seat. This is not an appropriate solution to the first and secondproblems. This reference also uses a structural means, so it isdifficult to meet the fourth requirement, and variation in structuraland dimensional tolerances may affect the control of releasing the gas.

From the analysis of the above six references, it can be seen that thereis no solution to the first problem and the second problem. In the firstreference and the third reference, the spring is installed in thepneumatic chamber, which can buffer the impact of the central portionagainst the valve seat. However, it cannot overcome the vibration whenthe high-pressure gas is released from the pneumatic chamber, and thereis a need for an adjustable mechanism to complete the fourthrequirement. In the fourth reference, the fifth reference and the sixthreference, the actions of opening and closing the valve are linked. Whenthe high-pressure gas in the pneumatic chamber is not released, thespring of the spring chamber has the maximum compression. Taking a1-inch valve as an example, the compression force is up to 70 kg and thegas pressure is above 5 bar. When the high-pressure gas in the pneumaticchamber is to be released, the high-pressure gas will be released in anunrestricted manner to generate the maximum gas vibration. When theratio of the internal high pressure to the air pressure of the externalpipeline is greater than 1.5, there will be ultrasonic detonation, andthe spring energy accumulated by the spring will be released at the sametime. At this time, the elastic force of the spring will push the pistonto move at the highest speed, and the diaphragm valve is subject to alot of vibration. When the central portion is close to the valve seat,the piston will decelerate sharply because of the air buffering effectfrom the restricted flow of the exhaust gas. But, the whole valve bodystill needs to bear the vibration of deceleration. At this time, the aircushion deceleration function hopes to provide the function of shockabsorption. In the whole process, the gas is released and the springaccelerates to generate the maximum vibration, and shock absorption isachieved only when decelerating. In this way, the function of shockabsorption in the whole process cannot be achieved. Therefore, the firstand second problems cannot be completely solved, and the fourthrequirement cannot be met.

The fourth reference has introduced a miniature valve mechanism, but itdoes not improve the above problems and lacks the adjustment of theopening and closing time of the diaphragm valve, namely, the fourthrequirement. The above references cannot meet the requirement forvibration control of the normally closed valve that is switched from theopen state to the closed state. That is, it is impossible to solve thefirst and second problems and meet the first, second, third, and fourthrequirements.

In the process from the closed state to the open state of the normallyopen valve, when the high-pressure gas is released from the pneumaticchamber, there will be severe ultrasonic vibration at the moment ofrelease.

The fourth reference doesn't mention whether the miniature valvemechanism can smoothly release the high-pressure gas of the normallyclosed valve and the normally open valve to immediately relieve such asituation and slow down the release of the elastic force of the springand continue to discharge the gas. It is impossible to meet such arequirement. It is also impossible to ensure that the central portion ofthe normally open valve is moved at a reasonable speed away from thevalve seat to slow down the turbulent flow, backflow and negativepressure generated near the valve seat. It is also impossible to ensurethat the central portion of the normally closed valve is moved at areasonable speed to approach the valve seat to slow down the jetgenerated near the valve seat. It is also questionable whether theresidual gas can be discharged quickly when the pressure is reduced forthe valve to be closed smoothly to short the whole stroke.

From the above description, the miniature valve mechanism needs to solvethe following problems in the whole process from the open state to theclosed state of the valve or in the whole process from the closed stateto the open state of the valve.

-   -   Third Problem: When the high-pressure gas is released, it should        react immediately to slow down the release of the high-pressure        gas and slow down the extension of the spring in the spring        chamber.    -   Fourth Problem: When the pressure of the high-pressure gas        decreases, the residual gas in the pneumatic chamber can be        discharged quickly.    -   Fifth Problem: When the pneumatic chamber is to be filled with        the high-pressure gas, the speed of gas filling is not affected.

The miniature valve mechanism set forth in the fourth reference is verysimilar to a common check valve with a spring mechanism, including avalve structure that can move a ball or a miniature piston or a spring,etc. In general, this mechanism is a ball check valve. In the prior art,there are many floating ball check valves developed on the market. Thefollowing are the references of the prior art:

Seventh Reference

European Patent No. EP0192474A2 titled “a valve” published in 1986relates to a check valve for engine gas fuel pipeline. It is a one-wayvalve, including a control ball, a valve chamber, an inlet pipe, anoutlet pipe, a valve seat and a ball seat. The valve chambercommunicates with the inlet and the outlet. The main control element isa metal control ball installed in the valve chamber. The ball seat isinstalled in a cavity of the valve chamber for accommodating the controlball. When the fuel is delivered at a normal flow rate, it will flowthrough one side of the control ball in the valve chamber, and thecontrol ball will be suspended in the valve chamber under the influenceof the flow rate. In the first embodiment, the valve seat is installedat the inlet on the inner side wall of the valve chamber. The inside ofthe outlet pipe in the valve chamber is provided with a protrusion sothat the ball does not obstruct the delivery of gaseous fuel. When thegas fuel delivery pipeline is ruptured, the high-pressure gas fuelflowing back from the engine to the check valve presses the control ballagainst the valve seat to seal and close the check valve. In the secondembodiment, the valve seat is installed at the inlet on the inner sidewall of the valve chamber. When the flow rate of the gas fuel exceeds1.5 times the normal value, the control ball will be pressed on thevalve seat to seal and close the check valve. In this reference, thecontrol ball closes the check valve only when the flow rate of the gasfuel exceeds the normal value, and it is not mentioned that the controlball will automatically fall under a certain compression ratio. Itcannot solve the third and fourth problems. The control ball of thisreference can float freely, which can be used as a two-way valve forrapid filling and can solve the fifth problem.

Eighth Reference

U.S. Pat. No. 4,120,315A titled “velocity check valve” published in 1978relates to a velocity check valve for oil or gas wells, used to preventleakage loss and fire loss, comprising a control ball, a valve chamber,an inlet, an outlet, an annular valve seat, a handle push rod and a ballseat. The valve chamber communicates with the inlet and the outlet. Themain control element is a metal control ball installed in the valvechamber. The ball seat is installed in the valve chamber foraccommodating the control ball. When the fuel is delivered at a normalflow rate, the control ball will be suspended in the valve chamber underthe influence of the flow rate. When the flow exceeds, the control ballwill close the velocity check valve. At this time, the control ballestablishes a pressure differential between the inlet and the outlet.When such a pressure differential is gradually reduced to near zero, thecontrol ball will automatically drop. If the pressure difference doesnot change, the handle push rod can be used to push the control valve toopen the velocity check valve. In this reference, the control ballcloses the check valve only when the flow exceeds the normal value. Whenthe pressure differential of the control ball is gradually reduced tonear zero, the control ball will automatically drop. It cannot solve thethird and fourth problems. The control ball of this reference can floatfreely, which can be used as a two-way valve for rapid filling and cansolve the fifth problem.

When the miniature mechanism is introduced to solve the first and secondproblems, the miniature mechanism itself needs to further overcome thethird, fourth, and fifth problems. The fifth problem can be solvedeasily. However, the fourth, fifth and sixth references do not have agood solution to the fifth question. The first, second, third, fourth,fifth, sixth, seventh, eighth references do not have a good solution tothe third and fourth questions. That is to say, there is no goodsolution to the first to fifth problems. The miniature valve mechanismneeds to be further improved, so as to meet the first to fourthrequirements, thereby achieving the unique requirements of clean fluidand particle suspension fluid delivery. The present invention relates toa buffer valve, which belongs to an innovative structure of a miniaturemechanism similar to a ball check valve. The present invention canprovide solutions to the first to fifth problems and meet the first tofourth requirements.

SUMMARY OF THE INVENTION

A buffer valve is a two-way valve. The buffer valve is installed on apneumatic diaphragm valve. The pneumatic diaphragm valve includes apneumatic cylinder, a diaphragm and a valve seat. The pneumatic cylinderis divided into a pneumatic chamber and a spring chamber by a piston. Aspring is disposed in the spring chamber. The pneumatic chamber and thespring chamber each have a breathing hole. The breathing hole of thepneumatic chamber is installed with the buffer valve. The buffer valveis provided with a gas connector for filling a high-pressure gas. Thebuffer valve is configured to adjust release of the high-pressure gas inthe pneumatic chamber without affecting a filling speed of thehigh-pressure gas in the pneumatic chamber. The buffer valve has a toolpart located on an outside of the buffer valve for mounting ordemounting the buffer valve and for mounting the gas connector. Thediaphragm is an integral structure, and has a circumferential portion, acentral portion and an elastic portion. The elastic portion has aΩ-shaped cross section with an arc-shaped curve.

For a normally closed valve, when the high-pressure gas is released, thebuffer valve can slow down a pressure shock wave generated by therelease of the high-pressure gas and violent impact of the centralportion of the diaphragm against the valve seat within a period of time,and an approach speed of the central portion of the diaphragm toward thevalve seat is reduced to reduce intense jet flow generated by the valveseat when it is closed.

For a normally open valve, when the high-pressure gas is released, thebuffer valve can slow down a pressure shock wave generated by therelease of the high-pressure gas and an instantaneous leaving speed ofthe central portion of the diaphragm away from the valve seat within aperiod of time, so as to slow down generation of local negative pressureand reduce generation of intense eddy flow and intense turbulent flow.

An inner flow channel of the buffer valve includes an inner micro gashole, an inner chamber, an outer gas hole, and a floating ball. Theinner flow channel is selectively in communication with the internalpneumatic chamber or the gas connector of an external high-pressure gassource. The long cylindrical inner chamber has an axis, an inner annularsurface, an inner end, and an outer end. The inner end communicates withthe pneumatic chamber through the inner micro gas hole. The inner microgas hole is disposed at a position deviating from the axis of the innerchamber and close to the inner annular surface. The outer end of theinner chamber communicates with the gas connector through the outer gashole. The outer gas hole is located on the axis of the inner chamber.The floating ball is disposed in the inner chamber and floats along withthe high-pressure gas. The floating ball has an outer diameter d1 lessthan an inner diameter D2 of the inner chamber, d1<D2.

The buffer valve has the following functions in operation, including ahigh-filling action, a shielding action, a releasing action (including areleasing mechanism), a shielding time Δt, and an adjusting mechanism.

The high-filling action is that when the pneumatic chamber is filledwith the high-pressure gas, the high-pressure gas enters the innerchamber through the outer gas hole from a high-pressure pipeline andpushes the floating ball to move toward the inner micro gas hole,without covering the inner micro gas hole, allowing the high-pressuregas to enter the pneumatic chamber to have the high-filling action.

The shielding action is that when the high-pressure gas is released fromthe pneumatic chamber, the high-pressure gas passes through the innermicro gas hole to enter the inner chamber and drives the floating ballto move toward the outer gas hole to cover the outer gas hole to slowdown the release of high-pressure gas. The shielding action is caused byan opening of the floating ball and an inner diameter d3 of the outergas hole to form a circular contact line C. The circular contact line Ccannot achieve an airtightness effect but reduces the speed of gasleakage. The shielding action is caused by a pressure difference ΔPbetween a gas pressure and a pipeline pressure to generate a pressingforce Fp on the floating ball. The pressing force Fp is equal to thepressure difference ΔP multiplied by a circular area of the circularcontact line C. In order to ensure the slow degassing, the outer end ofthe inner chamber may also be provided with a micro gas hole tocommunicate with the gas connector, and the cross-sectional area of themicro gas hole is not greater than 50% of the cross-sectional area ofthe inner micro gas hole.

The releasing action is that when the high-pressure gas is continuouslyreleased under the shielding action, after the gas pressure is reduced,the releasing action is to release the pressing force Fp through thereleasing mechanism, so that the floating ball is displaced and nolonger covers the outer gas hole, and the residual high-pressure gas isdischarged quickly. The releasing mechanism is a mechanism using atleast one of a weight W of the floating ball, an elastic force Fs and amagnetic force Fm to resist the pressing force Fp and move the floatingball to complete the releasing action.

The shielding time Δt is a period from the generation of the shieldingaction to the completion of the releasing action. In the process from anopen state to a closed state of the normally closed valve and in theprocess from the closed state to the open state of the normally openvalve, the period of time is that when the high-pressure gas isreleased, the shielding time Δt of the buffer valve is to slow down thepressure shock wave generated by the release of the high-pressure gas inthe whole process. The approach speed of the central portion of thediaphragm of the normally closed valve toward the valve seat is reducedin the whole process to reduce impact and to reduce intense jet flowgenerated by the valve seat when it is closed. The leaving speed of thecentral portion of the diaphragm of the normally open valve away fromthe valve seat is reduced in the whole process to slow down generationof local negative pressure and reduce generation of intense eddy flowand intense turbulent flow.

The adjusting mechanism is that the length of the shielding time Δt isadjusted through the weight W of the floating ball, the elastic force Fsand the magnetic force Fm of the releasing action.

A straight line L1 is defined from the circular contact line C to thecenter of the floating ball. A straight line L2 is defined from thecenter of the floating ball to the center of the inner diameter d3 ofthe outer gas hole. An included angle θ is defined between the straightline L1 and the straight line L2. That is, the center of the floatingball 23 is connected to the circular contact line C to form a cone angle2θ. The circular contact line is a narrow annular band structure, forexample, a chamfer is formed at the opening of the inner diameter d3 ofthe outer gas hole. When the outer diameter d1 of the floating ball isless than the inner diameter d3 of the outer gas hole, d1<d3, the areaof the circular contact line C is equal to the cross-sectional area ofthe outer diameter of the floating ball. The annular area of a gapbetween the outer diameter d1 and the inner diameter d3 is not greaterthan 50% of the cross-sectional area of the inner micro gas hole toachieve slow degassing. The length of the shielding time Δt of theshielding action is proportional to the pressing force Fp. The length ofthe shielding time Δt of the shielding action is proportional to thesize of the cone angle 2θ.

When the releasing mechanism uses the weight W of the floating ball, theshielding action is that when the weight W of the floating ball cannotresist the pressing force Fp, the floating ball is secured to the outergas hole, and the releasing mechanism is that when the pressing force Fpgenerated by the pressure difference ΔP cannot resist the weight W ofthe floating ball, the floating ball is displaced to the inner chamberand no longer covers the outer gas hole.

When the releasing mechanism uses the elastic force Fs, the shieldingaction is that when the elastic force Fs borne by the floating ballcannot resist the pressing force Fp, the floating ball is secured to theouter gas hole, and the releasing mechanism is that when the pressingforce Fp generated by the pressure difference ΔP cannot resist theelastic force Fs borne by the floating ball, the floating ball isdisplaced to the inner chamber and no longer covers the outer gas hole.

When the releasing mechanism uses the magnetic force Fm, the shieldingaction is that when the magnetic force Fm borne by the floating ballcannot resist the pressing force Fp, the floating ball is secured to theouter gas hole, and the releasing mechanism is that when the pressingforce Fp generated by the pressure difference ΔP cannot resist themagnetic force Fm borne by the floating ball, the floating ball isdisplaced to the inner chamber and no longer covers the outer gas hole.

First Embodiment

This embodiment is further described according to the summary of theinvention. The buffer valve includes a miniature valve body, thebreathing hole and the floating ball. The miniature valve body has acylindrical shape and includes the inner chamber, an outer chamber, apartition portion, and the outer gas hole. The outer chamber isconfigured to install the gas connector. The breathing hole includes aninner accommodating chamber and the inner micro gas hole. The breathinghole is disposed on an outer ring wall of the pneumatic chamber. Theinner micro gas hole is disposed at a position where the inneraccommodating chamber deviates from the axis of the inner chamber and isclose to the inner annular surface. An outer ring surface of theminiature valve body is coupled and sealed with the inner accommodatingchamber of the breathing hole. The partition portion is located in themiddle of the miniature valve body to separate the inner chamber and theouter chamber at two ends. The partition portion has the outer gas holeto communicate with the inner chamber and the outer chamber. The outergas hole is located on the axis.

Second Embodiment

This embodiment is further described according to the summary of theinvention. The buffer valve includes a miniature valve body, a breathingcover and the floating ball. The miniature valve body has a cylindricalshape and includes the inner chamber, an outer chamber, a partitionportion, and the outer gas hole. The breathing cover is configured toconnect the breathing hole and includes an inner accommodating chamber,the inner micro gas hole, and an external thread. An external thread ofthe breathing cover is coupled and sealed with the breathing hole. Theinner micro gas hole is located on the breathing cover at a positionwhere the inner accommodating chamber deviates from the axis of theinner chamber and is close to the inner annular surface to communicatewith the breathing hole. An outer ring surface of the miniature valvebody is coupled and sealed with the inner accommodating chamber of thebreathing cover. The outer chamber is configured to install the gasconnector. The partition portion is located in the middle of theminiature valve body to separate the inner chamber and the outer chamberat two ends. The partition portion has the outer gas hole to communicatewith the inner chamber and the outer chamber. The outer gas hole islocated on the axis.

As described in the first embodiment and the second embodiment, theshielding action is that when the weight W of the floating ball cannotresist the pressing force Fp, the floating ball is secured to the outergas hole. As described in the first embodiment and the secondembodiment, the releasing action and the releasing mechanism are thatwhen the weight W of the floating ball exceeds the pressing force Fpgenerated by the pressure difference ΔP, the floating ball is displacedto the inner chamber and no longer covers the outer gas hole.

As described in the first embodiment and the second embodiment, thereleasing action is reliably completed due to the ratio of the outerdiameter d1 of the floating ball to the inner diameter D2 of the innerchamber, d1/D2≤0.6.As described in the first embodiment and the secondembodiment, the outer diameter d1 of the floating ball is greater thanthe outer diameter d3 of the outer gas hole, and the cone angle 20,10°≤θ≤60°.

As described in the first embodiment and the second embodiment, theadjusting mechanism is configured to adjust parameters including theweight W and the outer diameter d1 of the floating ball and the coneangle 2θ.

Third Embodiment

This embodiment is further described according to the summary of theinvention. The buffer valve includes a miniature valve body, thebreathing hole, the floating ball, a releasing mechanism, a retainingring, and an adapter. The miniature valve body has a cylindrical shapeand includes the inner chamber, a connecting chamber, a partitionportion, and the outer gas hole. The breathing hole includes the inneraccommodating chamber and the inner micro gas hole. The breathing holeis disposed on an outer ring wall of the pneumatic chamber. An outerring surface of the miniature valve body is coupled and sealed with theinner accommodating chamber of the breathing hole. The inner micro gashole is disposed at a position where the inner accommodating chamberdeviates from the axis of the inner chamber and is close to the innerannular surface. The partition portion is disposed between the innerchamber and the connecting chamber. The partition portion has the outergas hole to communicate with the connecting chamber and the innerchamber. The outer gas hole is located on the axis. An inner diameter ofthe connecting chamber is greater than that of the inner chamber. Theretaining ring and the adapter are secured in an airtightness manner.The adapter is installed at an open end of the connecting chamber and islocated outside the retaining ring. The adapter is configured to connectthe gas connector and the high-pressure pipeline and communicates withthe pneumatic chamber. The retaining ring has a cylindrical shape andincludes a shaft hole and at least one ventilation hole. The retainingring is secured to a bottom of the connecting chamber and pressedagainst the partition portion. The shaft hole has an inner diameter lessthan that of the outer gas hole. The ventilation hole is incommunication with the outer gas hole. The releasing mechanism includesan adjusting shaft, the retaining ring, a retaining nut set, and aminiature spring. The adjusting shaft includes an external thread, aball seat, and a shaft. The disc-shaped ball seat is located at one endof the adjusting shaft and has a concave spherical surface. The externalthread is located at another end of the adjusting shaft. In assembly,the retaining ring is firstly locked inside the connecting chamber. Theadjusting shaft is inserted in the miniature spring with its tail endpassing through the outer gas hole and the shaft hole from the side ofthe inner chamber, so that the external thread is located in theconnecting chamber to keep the ball seat at the side of the innerchamber. The miniature spring is sleeved on the shaft and pressedbetween the ball seat and the retaining ring. The inner diameter of theouter gas hole is greater than an outer diameter of the ball seat, sothat the adjusting shaft can move back and forth in the inner chamberand the outer gas hole freely. The shaft is in sliding fit with theshaft hole to support the adjusting shaft. The external thread of theadjusting shaft extends out of the shaft hole. The retaining nut set isdisposed on the external thread to ensure that the adjusting shaft willnot be loosened from the retaining ring when the high-pressure gas isfilled.

Fourth Embodiment

This embodiment is further described according to the summary of theinvention. The buffer valve includes a miniature valve body, thebreathing hole, the floating ball, a releasing mechanism, a retainingring, a slide sleeve, and an adapter. The miniature valve body has acylindrical shape and includes the inner chamber, a connecting chamber,a partition portion, and the outer gas hole. The breathing hole includesan inner accommodating chamber and the inner micro gas hole. Thebreathing hole is disposed on an outer ring wall of the pneumaticchamber. An outer ring surface of the miniature valve body is coupledand sealed with the inner accommodating chamber of the breathing hole.The inner micro gas hole is disposed at a position where the inneraccommodating chamber deviates from the axis of the inner chamber and isclose to the inner annular surface. The partition portion is disposedbetween the inner chamber and the connecting chamber. The partitionportion has the outer gas hole to communicate with the outer chamber andthe connecting chamber. An inner diameter of the connecting chamber isgreater than that of the inner chamber. The retaining ring and theadapter are secured in an airtightness manner. The adapter is installedat an open end of the connecting chamber and is located outside theretaining ring. The adapter is configured to connect the gas connectorand the high-pressure pipeline and communicates with the pneumaticchamber. The retaining ring has a cylindrical shape and includes atleast one ventilation hole and a central screw hole. The retaining ringis secured to a bottom of the connecting chamber and pressed against thepartition portion. The central screw hole has an inner diameter lessthan that of the outer gas hole, and is in communication with the outergas hole. The releasing mechanism has an adjusting shaft, the slidesleeve, the retaining ring, a locking nut, the retaining nut set, and aminiature spring. The adjusting shaft includes an external thread, aball seat, and a shaft. The disc-shaped ball seat is located at one endof the adjusting shaft and has a concave spherical surface. The externalthread is located at another end of the adjusting shaft. The slidesleeve includes a slide shaft hole, an adjusting disc, and an externalthread. In assembly, the retaining ring is firstly locked inside theconnecting chamber. The locking nut is fitted on the external thread ofthe slide sleeve and screwed to the position of the adjusting disc. Theexternal thread of the slide sleeve is coupled with the central screwhole of the retaining ring. The adjusting shaft is inserted in theminiature spring with its tail end to pass through the outer gas holeand the slide shaft hole from the side of the inner chamber, so that theexternal thread is located in the connecting chamber to keep the ballseat at the side of the inner chamber. An outer diameter of the externalthread of the slide sleeve is greater than an outer diameter of theminiature spring. The miniature spring is sleeved on the shaft andpressed between the ball seat and the slide sleeve. The inner diameterof the outer gas hole is greater than an outer diameter of the ballseat, so that the adjusting shaft can move back and forth in the innerchamber and the outer gas hole freely. The shaft is in sliding fit withthe slide shaft hole to support the adjusting shaft. The adjusting discof the slide sleeve is rotated to move forward or rearward and issecured by the locking nut. The position of the miniature spring islinked with the position of the slide sleeve to change a compressiondisplacement ΔX. The external thread of the adjusting shaft extends outof the slide shaft hole of the slide sleeve. The retaining nut set isdisposed on the external thread to ensure that the adjusting shaft willnot be loosened from the slide sleeve when the high-pressure gas isfilled. The position of the slide sleeve is adjusted to fine-tune thecompression displacement ΔX of the miniature spring to change theelastic force Fs. When the value of the elastic coefficient K of theminiature spring is fixed and the outer diameter d1 and weight W of thefloating ball are also fixed, the elastic force Fs can be changed toadjust the length of the shielding time Δt.

As described in the third embodiment and the fourth embodiment, theshielding action is that when the high-pressure gas brings the floatingball to be attached to the ball seat, a pressing force Fp generated bythe pressure difference ΔP generated by the high-pressure gas is appliedto the floating ball. The miniature spring is pushed back by the ballseat to generate a compression displacement ΔX and the elastic force Fs.The compression displacement ΔX is the compression amount of theminiature spring, Fp Fs. As described in the third embodiment and thefourth embodiment, the releasing action and releasing mechanism is thatwhen the pressing force Fp generated by the pressure difference ΔPcannot resist the elastic force Fs of the miniature spring, Fp Fs, thefloating ball is pushed away and moved to the inner chamber withoutcovering the outer gas hole.

As described in the third embodiment and the fourth embodiment, thereleasing mechanism is not restricted by the direction of the weight Wof the floating ball and the direction of the pressing force Fp.

As described in the third embodiment and the fourth embodiment, thereleasing mechanism is reliably completed due to the ratio of the outerdiameter d1 of the floating ball to the inner diameter D2 of the innerchamber, d1/D2≤0.8. As described in the third embodiment and the fourthembodiment, the outer diameter d1 of the floating ball is greater thanthe inner diameter d3 of the outer gas hole, the cone angle 20,15°≤θ≤80°.

As described in the third embodiment and the fourth embodiment in theadjusting mechanism, the shielding time Δt is adjusted by the weight Wand the outer diameter d1 of the floating ball and the elastic force Fsof the miniature spring, and the adjustment of the elastic force Fsrefers to adjusting the elastic coefficient of the miniature spring. Asdescribed in the third embodiment and the fourth embodiment, theadjusting mechanism includes the retaining nut set. The relativeposition of the ball seat of the adjusting shaft relative to an openingof the outer gas hole at the side of the inner chamber can be set toensure that the floating ball can indeed complete the shielding actionand the releasing action.

Fifth Embodiment

This embodiment is further described according to the summary of theinvention. The buffer valve includes a miniature valve body, a breathingcover, and a floating ball. The floating ball has a cylindrical shapeand includes a spherical curved surface at its front end and a cylinderat its rear end. The cylinder has a cylindrical blind hole. A magneticring is installed inside the floating ball. The magnetic ring is a longring located near the spherical curved surface. The center of themagnetic ring and is concentric with the blind hole. The miniature valvebody has a cylindrical shape and includes the inner chamber, an outerchamber, a partition portion, the outer gas hole, and a magnetic member.The outer chamber is configured to mount the gas connector. Thepartition portion is located in the middle of the miniature valve bodyto separate the inner chamber and the outer chamber at two ends. Theinner chamber and the outer chamber are in communication with each otherthrough the outer gas hole. The outer gas hole is located at the centerof the partition portion. The magnetic member is annular and is mountedon one side of the partition portion close to the inner chamber and isconcentric with the outer gas hole. The breathing cover is configured toconnect the breathing hole and includes an inner accommodating chamber,the inner micro gas hole, an external thread, and a central post. Theexternal thread of the breathing cover is coupled and sealed with thebreathing hole. The inner micro gas hole is located on the breathingcover and deviated from the axis of the inner accommodating chamber andis close to the inner annular surface to communicate with the breathinghole. The central post of the breathing cover is mounted at a centralposition of a bottom of the inner accommodating chamber and extends intothe inner chamber and is fitted in the blind hole of the floating ball.An outer ring surface of the miniature valve body is coupled and sealedwith the inner accommodating chamber of the breathing cover. Thefloating ball is disposed in the inner flow channel and can move backand forth on the central post.

A mutually repulsive magnetic force Fm is generated between the magneticring of the floating ball and the magnetic member of the miniature valvebody. The shielding action is that when the magnetic force Fm mutuallyrepelling the magnetic ring of the floating ball and the magnetic memberof the miniature valve body cannot resist the pressing force Fpgenerated by the pressure difference ΔP, Fm<Fp, the floating ball issecured to the outer gas hole. The releasing mechanism is that when thepressing force Fp generated by the pressure difference ΔP cannot resistthe magnetic force Fm mutually repelling the magnetic ring and themagnetic member, Fm>Fp, the floating ball is displaced backward to theinner chamber and no longer covers the outer gas hole. As described inthe fifth embodiment, the releasing mechanism is not restricted by thedirection of the weight W of the floating ball and the direction of thepressing force Fp.

As described in the fifth embodiment, the releasing action is reliablycompleted due to the ratio of the outer diameter d1 of the floating ballto the inner diameter D2 of the inner chamber, d1/D2≤0.8. As describedin the fifth embodiment, when the outer diameter d1 of the floating ballis greater than the inner diameter d3 of the outer gas hole, the coneangle 20, 15°≤θ≤80°.

As described in the fifth embodiment, in the adjusting mechanism, theshielding time Δt is adjusted by the weight W and the outer diameter d1of the floating ball and the magnetic force Fm. The adjusting mechanismof the magnetic force Fm refers to adjusting a mutual repulsive forcebetween the magnetic ring and the magnetic member of the miniaturevalve.

The summary of the invention and the embodiments of the invention cansolve the first, second, third, fourth and fifth problems, and fullymeet the first, second, third and fourth requirements, thereby meetingthe unique needs of clean fluid and particle suspension fluidtransportation. The invention will be further described below withseveral embodiments.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a sectional view of the pneumatic diaphragm valve;

FIG. 2 is a sectional view of the breathing hole;

FIG. 3A is a schematic view illustrating the positions of the floatingball and the inner micro gas hole when the pneumatic chamber is filledwith the gas;

FIG. 3B is a schematic view illustrating the floating ball, the outergas hole and the cone angle 20 in the beginning of releasing thehigh-pressure gas;

FIG. 3B′ is a partial enlarged view of FIG. 3B;

FIG. 3C is a schematic view illustrating the positions of the floatingball and the inner chamber at the end of releasing the high-pressuregas;

FIG. 4 is a cross-sectional view of the buffer valve 2 a of the firstembodiment;

FIG. 5 is a cross-sectional view of the buffer valve 2 b of the secondembodiment;

FIG. 6A is a cross-sectional view of the buffer valve 2 c of the thirdembodiment, particularly to the miniature valve body 21 c;

FIG. 6B is a schematic view illustrating the floating ball, the outergas hole and the cone angle 2θ in the beginning of releasing thehigh-pressure gas of the buffer valve 2 e in the third embodiment;

FIG. 6B′ is a partial enlarged view of FIG. 6B;

FIG. 6C is a schematic view illustrating the positions of the floatingball and the inner chamber at the end of releasing the high-pressure gasof the buffer valve 2 e in the third embodiment;

FIG. 6C′ is a partial enlarged view of FIG. 6C;

FIG. 7A is a cross-sectional view of the buffer valve 2 d of the fourthembodiment, particularly to the miniature valve body 21 d;

FIG. 7B is a schematic view illustrating the floating ball, the outergas hole and the cone angle 2θ in the beginning of releasing thehigh-pressure gas of the buffer valve 2 d in the fourth embodiment;

FIG. 7B′ is a partial enlarged view of FIG. 7B;

FIG. 7C is a schematic view illustrating the positions of the floatingball and the inner chamber at the end of releasing the high-pressure gasof the buffer valve 2 e in the fourth embodiment;

FIG. 7C′ is a partial enlarged view of FIG. 7C;

FIG. 8A is a cross-sectional view of the buffer valve 2 e of the fifthembodiment;

FIG. 8B is a cross-sectional view of the miniature valve body 21 e ofthe fifth embodiment;

FIG. 8C is a schematic view illustrating the floating ball, the outergas hole and the cone angle 2θ in the beginning of releasing thehigh-pressure gas of the buffer valve 2 e in the fifth embodiment;

FIG. 8C′ is a partial enlarged view of FIG. 8C;

FIG. 8D is a schematic view illustrating the positions of the floatingball and the inner chamber at the end of releasing the high-pressure gasof the buffer valve 2 e in the fifth embodiment; and

FIG. 8D′ is a partial enlarged view of FIG. 8C.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Embodiments of the present invention will now be described, by way ofexample only, with reference to the accompanying drawings.

For all the descriptions, please refer to FIG. 1 , FIG. 2 , FIG. 3A,FIG. 3B, FIG. 3B′, FIG. 3C, FIG. 4 , FIG. 5 , FIG. 6A, FIG. 6B, FIG.6B′, FIG. 6C, FIG. 6C′, FIG. 7A, FIG. 7B, FIG. 7B′, FIG. 7C, FIG. 7C′,FIG. 8A, FIG. 8B, FIG. 8C, FIG. 8C′, FIG. 8D, and FIG. 8D′.

Please refer to FIG. 1 and FIG. 2 . The schematic views of the followingembodiments all take the normally closed valve as an example. Therelevant application of the normally open valve is supplemented by theliteral description. The present invention is a buffer valve 2, which isa two-way valve. The buffer valve 2 is installed on a pneumaticdiaphragm valve 1 for adjusting the release of the high-pressure gaswithout affecting a high-filling action 236 of the high-pressure gas.(The high-filling action 236 is shown in FIG. 3A.) The pneumaticdiaphragm valve 1 includes a pneumatic cylinder 10, a diaphragm 11, anda valve seat 12. The pneumatic cylinder 10 is divided into a pneumaticchamber 14 and a spring chamber 15 by a piston 13. A spring 151 isdisposed in the spring chamber 15. The spring chamber 15 has a breathinghole 152. The pneumatic chamber 14 has a breathing hole 141. Thediaphragm 11 is an integral structure, having a circumferential portion111, a central portion 112 and an elastic portion 113. The elasticportion 113 has a Ω-shaped cross section with an arc-shaped curve 114.The buffer valve 2 is installed in the breathing hole 141 of thepneumatic chamber 14 to adjust the flow rate of the breathing hole 141.

When the high-pressure gas is released in the pneumatic diaphragm valve1 of the normally closed valve, the buffer valve 2 can slow down thepressure shock wave generated by the release of the high-pressure gasand the violent impact of the central portion 112 against the valve seat12 within a certain period of time. When the high-pressure gas isreleased in the pneumatic diaphragm valve 1 of the normally open valve,the buffer valve 2 can slow down the pressure shock wave generated bythe release of the high-pressure gas and the instantaneous leaving speedof the central portion 112 from the valve seat 12 within a period oftime, and can slow down the generation of local negative pressure andreduce the generation of intense eddy flow and intense turbulent flow.The period of time is preferably when the high-pressure gas is released,the buffer valve 2 is actuated immediately, and is actuated throughoutthe entire process. In the normally closed valve, the approach speed ofthe central portion 112 of the diaphragm 11 to the valve seat 12 isreduced throughout the entire process to reduce the impact. In thenormally open valve, the leaving speed of the central portion 112 of thediaphragm 11 from the valve seat 12 is reduced throughout the entireprocess, which can reduce the generation of local negative pressure.

A gas connector 16 is installed on the buffer valve 2 for connecting toa high-pressure pipeline 161. The outside of the buffer valve 2 has atool part. The tool part is used for installing or removing the buffervalve 2 and the gas connector 16.

Please refer to FIG. 2 . An inner flow channel 22 of the buffer valve 2includes an inner micro gas hole 221, an inner chamber 222, an outer gashole 227, and a floating ball 23. The inner flow channel 22 isselectively in communication with the internal pneumatic chamber 14 orthe gas connector 16 of an external high-pressure gas source.

The long cylindrical inner chamber 222 has an axis 223, an inner annularsurface 224, an inner end 225, and an outer end 226. The inner micro gashole 221 is installed on the inner end 225 and communicates with thepneumatic chamber 14. The inner micro gas hole 221 is disposed at aposition deviating from the axis 223 of the inner chamber 222 and closeto the inner annular surface 224. The outer gas hole 227 is disposed onthe outer end 226 and located on the axis 223. The outer gas hole 227 isin communication with the gas connector 16. The floating ball 23 isdisposed in the inner chamber 222 and floats along with thehigh-pressure gas flow. The floating ball 23 has an outer diameter d1less than an inner diameter D2 of the inner chamber, d1<D2.

The buffer valve 2 has the following functions in operation, including ahigh-filling action 236, a shielding action 230, a releasing action 231,a shielding time Δt, an adjusting mechanism 28, and a releasingmechanism 24.

Please refer to FIG. 3A. The high-filling action 236 is that when thepneumatic chamber 14 is filled with the high-pressure gas, a gas flow142 of the high-pressure gas enters the inner flow channel 22 throughthe outer gas hole 227 from the gas connector 16 and pushes the floatingball 23 to be at the inner end 225 of the inner chamber 222, withoutcovering the inner micro gas hole 221, allowing the high-pressure gas toenter the pneumatic chamber 14 through the inner micro gas hole 221 tohave the high-filling action 236.

Please refer to FIG. 3B and FIG. 3B′. The shielding action 230 is thatwhen the high-pressure gas is released from the pneumatic chamber 14,the high-pressure gas passes through the inner micro gas hole 221 toenter the inner flow channel 22, and drives the floating ball 23 to moveto the outer gas hole 227 and generates the shielding action 230 to slowthe release of high-pressure gas flow. The shielding action 230 iscaused by the opening of the floating ball 23 and the inner diameter d3of the outer gas hole 227 to form a circular contact line C without asealing surface. The circular contact line C cannot achieve the effectof airtightness but reduces the speed of gas leakage.

Please refer to FIG. 3B′. A straight line L1 is defined from thecircular contact line C to the center of the floating ball 23. Astraight line L2 is defined from the center of the floating ball 23 tothe center of the inner diameter d3 of the outer gas hole 227. Thestraight line L2 is approximately concentric with the axis 223. Anincluded angle θ is defined between the straight line L1 and thestraight line L2. That is, the center of the floating ball 23 isconnected to the circular contact line C to form a cone angle 2θ, whichis twice the included angle θ. The shielding action 230 is caused by apressure difference ΔP between the gas pressure and the pipelinepressure to generate a pressing force Fp on the floating ball 23. Thepressing force Fp is equal to the pressure difference ΔP multiplied bythe circular area of the circular contact line C. The circular contactline C may be a narrow annular band structure without an airtightfunction. For example, the annular band structure forms a chamfer at theopening of the inner diameter d3 of the outer gas hole 227. When theouter diameter d1 of the floating ball 23 is less than the innerdiameter d3 of the outer gas hole 227, d1<d3, the area of the circularcontact line C is equal to the cross-sectional area of the outerdiameter of the floating ball 23. At this time, the annular area of theunilateral gap is not greater than 50% of the cross-sectional area ofthe inner micro gas hole 221 to achieve slow degassing. In order toensure the slow degassing, the outer end of the inner chamber 222 mayalso be provided with a micro gas hole 217 to communicate with the gasconnector 16, and the cross-sectional area of the micro gas hole 217 isnot greater than 50% of the cross-sectional area of the inner micro gashole 221.

Please refer to FIG. 3B′ and FIG. 3C. The releasing action 231 is thatwhen the high-pressure gas is continuously released under the shieldingaction 230, the shielding action 230 is replaced by the releasing action231 after the gas pressure is reduced and the pressure difference ΔPwith the pipeline pressure is reduced for residual high-pressure gas tobe discharged quickly. The releasing action 231 is to release thepressing force Fp through the releasing mechanism 24, so that thefloating ball 23 is displaced and no longer shielded, and the residualhigh-pressure gas can be released quickly.

The releasing mechanism 24 refers to a mechanism using at least one ofthe weight W of the floating ball, an elastic force Fs and a magneticforce Fm to resist the pressing force Fp and move the floating ball 23to complete the releasing action 231.

The shielding time Δt refers to the period from the generation of theshielding action 230 to the completion of the releasing action 231.

The adjusting mechanism 28 refers to that the length of the shieldingtime Δt is adjusted through the weight W, the elastic force Fs or themagnetic force Fm of the floating ball 23 of the releasing action 231.

The length of the shielding time Δt of the shielding action 230 isproportional to the pressing force Fp. The length of the shielding timeΔt of the shielding action 230 is proportional to the size of the coneangle 2θ.

When the releasing mechanism 24 uses the weight W of the floating ball23, it is called the releasing mechanism 24 a. The shielding action 230is that when the weight W of the floating ball 23 cannot resist thepressing force Fp, the floating ball 23 is secured to the outer gas hole227. The releasing mechanism is that when the pressing force Fpgenerated by the pressure difference ΔP cannot resist the weight W ofthe floating ball 23, the floating ball 23 is displaced to the innerchamber 222 and no longer covers the outer gas hole 227.

When the releasing mechanism 24 uses the elastic force Fs, it is calledthe releasing mechanism 24 b/24 c. The shielding action 230 is that whenthe elastic force Fs borne by the floating ball 23 cannot resist thepressing force Fp, the floating ball 23 is secured to the outer gas hole227. The releasing mechanism is that when the pressing force Fpgenerated by the pressure difference ΔP cannot resist the elastic forceFs borne by the floating ball 23, the floating ball 23 is displaced tothe inner chamber 222 and no longer covers the outer gas hole 227.

When the releasing mechanism 24 uses the magnetic force Fm, it is calledthe releasing mechanism 24 d. The shielding action 230 is that when themagnetic force Fm borne by the floating ball 23 cannot resist thepressing force Fp, the floating ball 23 is secured to the outer gas hole227. The releasing mechanism is that when the pressing force Fpgenerated by the pressure difference ΔP cannot resist the magnetic forceFm borne by the floating ball 23, the floating ball 23 is displaced tothe inner chamber 222 and no longer covers the outer gas hole 227.

For the normally open valve and the normally closed valve, during thehigh-speed filling action 236 of the high-pressure gas, the more thespring 151 in the spring chamber 15 is compressed, the higher therebound force will be. Such a rebound force provides a good bufferingeffect, and there will not be too much impact. The pneumatic chamber 14is subjected to a gradually rising pressure to reduce the vibration ofthe high-pressure gas.

Referring to FIG. 1 , for a normally closed valve, the approach speed115 of the central portion 112 is slowed down to reduce the impactagainst the valve seat 12, the jet flow generated by the water hammereffect is reduced, the transmission of pressure waves transmitted to thepipeline the upstream and downstream is reduced, and the service life ofequipment or joints is prolonged to improve reliability. There will notbe too many particles released to contaminate the clean fluid.

Referring to FIG. 1 , for a normally open valve, the leaving speed 116of the central portion 112 is slowed down to reduce the generation ofshort-term negative pressure vacuum and to reduce the short-term intenseturbulent flow and eddy flow of the fluid.

First Embodiment

Please refer to FIG. 4 . The buffer valve 2 a includes a miniature valvebody 21 a, the breathing hole 141 and the floating ball 23 (thereleasing mechanism 24 a). The breathing hole 141 includes an inneraccommodating chamber 143 and the inner micro gas hole 221. Theminiature valve body 21 a has a cylindrical shape, and includes theinner chamber 222, the outer gas hole 227, an outer chamber 212, apartition portion 213, an internal thread 216 and an external thread215. The breathing hole 141 is disposed on the outer ring wall of thepneumatic chamber 14. The inner micro gas hole 221 is disposed at aposition where the inner accommodating chamber 143 deviates from theaxis 223 of the inner chamber 222 and is close to the inner annularsurface 224 to communicate with the interior of the pneumatic chamber14. The inner accommodating chamber 143 has the internal thread 216. Thefloating ball 23 is installed in the inner chamber 222. The longcylindrical inner chamber 222 has the axis 223, the inner annularsurface 224, the inner end 225 and the outer end 226. The partitionportion 213 is located in the middle of the miniature valve body 21 a toseparate the inner chamber 222 and the outer chamber 212 at two ends.The outer gas hole 227 is disposed on the partition portion 213 andlocated on the axis 223. The outer gas hole 227 communicates with theinner chamber 222 and the outer chamber 212. The outer ring surface ofthe inner chamber 222 has the external thread 215 which is coupled andsealed with the internal thread of the inner accommodating chamber 143of the breathing hole 14. The outer chamber 212 has the internal thread216 for installing the gas connector 16. The partition part 213 can alsobe provided with the micro gas hole 217, the micro gas hole 217 isconnected to the inner chamber 222 and the outer chamber 212. The microgas hole 217 is used to ensure the slow leakage of gas; specifically,the two opposite ends of the micro gas hole 217 communicating with theinner chamber 222 and the outer chamber 212 have a largercross-sectional area and a smaller cross-sectional area at the middlesection, for example, the cross-sectional area of the opposite ends ofthe micro gas hole 217 is twice the cross-sectional area of the middlesection.

Second Embodiment

Please refer to FIG. 5 . The buffer valve 2 b is further evolved into anindependent device. The buffer valve 2 b includes a miniature valve body21 b, a breathing cover 20 a and the floating ball 23 (the releasingmechanism 24 a). The breathing cover 20 a includes an inneraccommodating chamber 202, the inner micro gas hole 221, and an externalthread 203. The breathing cover 20 a is configured to connect thebreathing hole 141 of the pneumatic chamber 14. The inner micro gas hole221 is disposed at a position away from the center of the bottom of theinner accommodating chamber 202 and communicates with the breathing hole141. The inner accommodating chamber 202 has an internal thread to becoupled and sealed with the miniature valve body 21 b. The miniaturevalve body 21 b has a cylindrical shape, and includes the inner chamber222, the outer gas hole 227, an outer chamber 212, a partition portion213, an external thread 215 and an internal thread 216. The floatingball 23 is installed in the inner chamber 222. The long cylindricalinner chamber 222 has the axis 223, the inner annular surface 224, theinner end 225 and the outer end 226. The outer ring surface of the innerchamber 222 has the external thread 215 which is coupled and sealed withthe internal thread of the inner accommodating chamber 202 of thebreathing cover 20 a. The partition portion 213 is located in the middleof the miniature valve body 21 b to separate the inner chamber 222 andthe outer chamber 212 at two ends. The outer gas hole 227 is disposed onthe partition portion 213 and located on the axis 223. The outer gashole 227 communicates with the inner chamber 222 and the outer chamber212. The outer chamber 212 has the internal thread 216 for installingthe gas connector 16.

As described in the first embodiment and the second embodiment shown inFIG. 4 and FIG. 5 , in conjunction with FIG. 3B, FIG. 3B′, and FIG. 3C,the shielding action 230 is that when the weight W of the floating ball23 cannot resist the pressing force Fp generated by the pressuredifference ΔP, the floating ball 23 is secured to the outer gas hole227. When the outer diameter d1 of the floating ball 23 is greater thanthe outer diameter d3 of the outer gas hole 227, the cone angle 2θ,10°≤θ≤60°. The releasing action 231 and the releasing mechanism 24 a arethat when the weight W of the floating ball 23 exceeds the pressingforce Fp generated by the pressure difference ΔP, the floating ball 23is displaced to the inner chamber 222 and no longer covers the outer gashole 227. The releasing action 231 can be reliably completed due to theratio of the outer diameter d1 of the floating ball 23 to the innerdiameter D2 of the inner chamber 222, d1/D2≤0.6. The adjusting mechanism28 is configured to adjust parameters such as the weight W and the outerdiameter d1 of the floating ball 23 and the cone angle 2θ, where thecone angle 2θ, 10°≤θ≤60°.

Third Embodiment

Please refer to FIG. 6A, FIG. 6B, FIG. 6B″, FIG. 6C and FIG. 6C′. Thebuffer valve 2 c includes a miniature valve body 21 c, the breathinghole 141, the floating ball 23, a releasing mechanism 24 b, a retainingring 25 a, and an adapter 27. The breathing hole 141 includes an inneraccommodating chamber 143 and the inner micro gas hole 221. Theminiature valve body 21 c has a cylindrical shape. The miniature valvebody 21 c includes the inner chamber 222, a connecting chamber 218, apartition portion 213, an outer gas hole 227, and an external thread215. The breathing hole 141 is disposed on the outer ring wall of thepneumatic chamber 14. The inner micro gas hole 221 is disposed at aposition where the inner accommodating chamber 143 deviates from theaxis 223 of the inner chamber 222 and is close to the inner annularsurface 224 to communicate with the interior of the pneumatic chamber14. The inner accommodating chamber 143 has an internal thread. The longcylindrical inner chamber 222 has the axis 223, the inner annularsurface 224, the inner end 225 and the outer end 226. The outer ringsurface of the inner chamber 222 has the external thread 215 which iscoupled and sealed with the internal thread of the inner accommodatingchamber 143. The floating ball 23 is installed in the inner chamber 222and floats along with the high-pressure gas flow. The outer diameter d1of the floating ball 23 is less than the inner diameter D2 of the innerchamber 222, d1<D2. The partition portion 213 is located in the middleof the miniature valve body 21 c to separate the inner chamber 222 andthe connecting chamber 218 at two ends. The outer gas hole 227 isdisposed on the partition portion 213 and located on the axis 223. Theouter gas hole 227 communicates with the inner chamber 222 and theconnecting chamber 218. The inner diameter of the connecting chamber 218is greater than that of the inner chamber 222. The inner annular spaceof the connecting chamber 218 is a cylindrical space or a steppedcylindrical space with different diameters. The retaining ring 25 a andthe adapter 27 can be locked and sealed through screw threads or otherfixing sealing methods. An open end of the adapter 27 installed in theconnecting chamber 218 is fixed in a tight and sealing manner and islocated outside the retaining ring 25 a for connecting the gas connector16 to deliver the high-pressure gas to the pneumatic chamber 14. Thecylindrical retaining ring 25 a includes a shaft hole 251, an outer ringsurface 252, and at least one ventilation hole 253. The outer ringsurface 252 has an external thread that can be engaged an internalthread of the bottom of the connecting chamber 218 and pressed againstthe partition portion 213. The inner diameter of the shaft hole 251 isless than the inner diameter of the outer gas hole 227, and theventilation hole 253 is not covered by the partition portion 213 and isin communication with the outer gas hole 227. The retaining ring 25 acan be tightened by applying torque from the open end of the connectingchamber 218 to a groove or recess (not shown) using a tool. The outerring surface 252 of the retaining ring 25 a and the inner surface of theconnecting chamber 218 may be smooth surfaces, and the two are coupledand slidably installed and secured to a sealing O-ring by a snap ring.The snap ring may be secured in the annular groove on the inner surfaceof the inner concave hole (not shown). The releasing mechanism 24 b hasan adjusting shaft 240, the retaining ring 25 a, a retaining nut set244, and a miniature spring 245. The adjusting shaft 240 includes anexternal thread 241, a ball seat 242, and a shaft 243. The disc-shapedball seat 242 is located at one end of the adjusting shaft 240 and has aconcave spherical surface. The external thread 241 is located at theother end of the adjusting shaft 240. The shaft 243 is located betweenthe ball seat 242 and the external thread 241. The inner diameter of theouter gas hole 227 is greater than the outer diameter of the ball seat242, so that the adjusting shaft 240 can move back and forth in theinner chamber 222 and the outer gas hole 227 freely.

In assembly, the retaining ring 25 a is firstly locked inside theconnecting chamber 218. The adjusting shaft 240 is inserted in theminiature spring 245 and its tail end passes through the outer gas hole227 and the shaft hole 251 from the side of the inner chamber 222, sothat the external thread 241 is located in the connecting chamber 218 tokeep the ball seat 242 at the side of the inner chamber 222. The innerdiameter d3 of the outer gas hole 227 is greater than the outer diameterof the ball seat 242, so that the adjusting shaft 240 can move back andforth in the inner chamber 222 and the outer gas hole 227 freely. Theshaft 243 is in sliding fit with the shaft hole 251 to support theadjusting shaft 240. The outer diameter of the ball seat 242 is greaterthan the outer diameter of the shaft 243 and the outer diameter of theminiature spring 245, so that the shaft 243 is inserted into theminiature spring 245, and the miniature spring 245 is pressed betweenthe ball seat 242 and the retaining ring 25 a. The external thread 241of the adjusting shaft 240 passing through the shaft hole 251 of theretaining ring 25 a extends out of the shaft hole 251. The retaining nutset 244 is disposed on the external thread 241 to ensure that theadjusting shaft 240 will not be loosened from the retaining ring 25 awhen the high-pressure gas is filled.

Fourth Embodiment

Please refer to FIG. 7A, FIG. 7B, FIG. 7B′, FIG. 7C and FIG. 7C′. Thebuffer valve 2 d includes a miniature valve body 21 d, the breathinghole 141, the floating ball 23, a releasing mechanism 24 c, a retainingring 25 b, a slide sleeve 26, and an adapter 27. The miniature valvebody 21 d includes the inner chamber 222, a connecting chamber 218, theouter gas hole 227, a partition portion 213, and an external thread 215.The breathing hole 141 includes an inner accommodating chamber 143 andthe inner micro gas hole 221. The breathing hole 141 is disposed on theouter ring wall of the pneumatic chamber 14. The inner micro gas hole221 is disposed at a position where the inner accommodating chamber 143deviates from the axis 223 of the inner chamber 222 and is close to theinner annular surface 224 to communicate with the interior of thepneumatic chamber 14. The inner accommodating chamber 143 has aninternal thread. The long cylindrical inner chamber 222 has the axis223, the inner annular surface 224, the inner end 225, and the outer end226. The outer ring surface of the inner chamber 222 has the externalthread 215 which is coupled and sealed with the internal thread of theinner accommodating chamber 143. The floating ball 23 is installed inthe inner chamber 222 and floats along with the high-pressure gas flow.The outer diameter d1 of the floating ball 23 is less than the innerdiameter D2 of the inner chamber 222, d1<D2. The partition portion 213is located in the middle of the miniature valve body 21 d to separatethe inner chamber 222 and the connecting chamber 218 at two ends. Theouter gas hole 227 is disposed on the partition portion 213 and locatedon the axis 223. The outer gas hole 227 communicates with the innerchamber 222 and the connecting chamber 218. The inner diameter of theconnecting chamber 218 is greater than that of the inner chamber 222.The inner annular space of the connecting chamber 218 is a cylindricalspace or a stepped cylindrical space with different diameters. Theretaining ring 25 a and the adapter 27 can be locked and sealed throughscrew threads or other fixing sealing methods. An open end of theadapter 27 installed in the connecting chamber 218 is fixed in a tightand sealing manner and is located outside the retaining ring 25 b forconnecting the gas connector 16 to deliver the high-pressure gas to thepneumatic chamber 14. The cylindrical retaining ring 25 b includes acentral screw hole 254, an outer ring surface 252, and at least oneventilation hole 253. The outer ring surface 252 has an external threadthat can be engaged an internal thread of the bottom of the connectingchamber 218 and pressed against the partition portion 213. The innerdiameter of the central screw hole 254 is less than the inner diameterof the outer gas hole 227, and the ventilation hole 253 is not coveredby the partition portion 213 and is in communication with the outer gashole 227. The retaining ring 25 b can be tightened by applying torquefrom the open end of the connecting chamber 218 to a groove or recess(not shown) using a tool. The outer ring surface of the retaining ring25 b and the inner surface of the connecting chamber 218 may be smoothsurfaces, and the two are coupled and slidably installed and secured toa sealing O-ring by a snap ring. The snap ring may be secured in theannular groove on the inner surface of the inner concave hole (notshown). The releasing mechanism 24 c has an adjusting shaft 240, theslide sleeve 26, the retaining ring 25 b, a locking nut 264, a retainingnut set 244, and a miniature spring 245. The slide sleeve 26 includes aslide shaft hole 261, an adjusting disc 262, and an external thread 263.The outer diameter of the outer thread 263 is greater than the outerdiameter of the miniature spring 245 and is coupled and sealed with thecentral screw hole 254. The inner diameter of the outer gas hole 227 isgreater than the outer diameter of the ball seat 242, so that theadjusting shaft 240 can move back and forth in the inner chamber 222 andthe outer gas hole 227 freely.

In assembly, the retaining ring 25 b is firstly locked inside theconnecting chamber 218. The external thread 263 of the slide sleeve 26is coupled and sealed with the central screw hole 254. The adjustingshaft 240 is inserted in the miniature spring 245 and its tail endpasses through the outer gas hole 227 and the slide shaft hole 251 fromthe side of the inner chamber 222, so that the external thread 241 islocated in the connecting chamber 218 to keep the ball seat 242 at theside of the inner chamber 222. The outer diameter of the ball seat 242is less than the inner diameter of the outer gas hole 227. The shaft 243is in sliding fit with the slide shaft hole 261 to support the adjustingshaft 240. The outer diameter of the ball seat 242 is greater than theouter diameter of the shaft 243 and the outer diameter of the miniaturespring 245, so that the shaft 243 is inserted into the miniature spring245, and the miniature spring 245 is pressed between the ball seat 242and the slide sleeve 26. The external thread 241 of the adjusting shaft240 passing through the slide shaft hole 261 extends out of the slideshaft hole 261. The retaining nut set 244 is disposed on the externalthread 241 to ensure that the adjusting shaft 240 will not be loosenedfrom the slide sleeve 26 when the high-pressure gas is filled. Theadjusting disc 262 of the slide sleeve 26 can be rotated to move forwardor rearward and can be secured by the locking nut 264. The position ofthe miniature spring 245 is linked with the position of the slide sleeve26 to change a compression displacement ΔX. The position of the slidesleeve 26 is adjusted to fine-tune the compression displacement ΔX ofthe miniature spring 245 to change the elastic force Fs. Therefore, whenthe value of the elastic coefficient K of the miniature spring 245 isfixed and the outer diameter d1 and weight W of the floating ball arealso fixed, the elastic force Fs can be changed to adjust the length ofthe shielding time Δt.

As described in the third embodiment and the fourth embodiment, theshielding action 230 is that when the high-pressure gas is released fromthe pneumatic chamber 14, the floating ball 23 will be attached to theball seat 242. When the floating ball 23 completes the shielding action,a circular contact line C is formed between the floating ball and theentrance of the outer gas hole 227. The shielding action 230 is causedby a pressing force Fp generated by the pressure difference ΔP betweenthe gas pressure and the pipeline pressure. The pressing force Fp actson the floating ball 23 and pushes the miniature spring 245 back throughthe ball seat 242 to generate the compression displacement ΔX. Thecompression displacement ΔX is the compression amount of the miniaturespring 245, and the miniature spring 245 generates the elastic force Fs,Fp Fs. The circular contact line C does not form a sealing surface andcannot achieve the effect of airtightness, but reduces the speed of gasleakage. When the outer diameter d1 of the floating ball 23 is greaterthan the inner diameter d3 of the outer gas hole, the cone angle 2θ isdefined between the circular contact line C generated by the shieldingaction 230 and the center of the floating ball 23, 15°≤θ≤80°. When theouter diameter d1 of the floating ball 23 is less than the innerdiameter d3 of the outer gas hole 227, the annular area of the gapbetween the outer diameter d1 and the inner diameter d3 is not greaterthan 50% of the cross-sectional area of the inner micro gas hole 221 toachieve slow degassing (not shown).

Please refer to FIG. 6B′, FIG. 6C′, FIG. 7B′, FIG. 7C′. The releasingaction 231 is that when the pressing force Fp generated by the pressuredifference ΔP cannot resist the elastic force Fs of the miniature spring245, Fp Fs, the floating ball 23 is pushed away and moved to the innerchamber 222 without covering the outer gas hole 227, so that theresidual high-pressure gas can be released quickly. The elastic force Fsis equal to the product of the compression displacement ΔX and theelastic coefficient K. The releasing action 231 can be reliablycompleted due to the ratio of the outer diameter d1 of the floating ball23 to the inner diameter D2 of the inner chamber 222, d1/D2 0.8.

In the adjusting mechanism 28, the shielding time Δt can be determinedby the weight W and the outer diameter d1 of the floating ball 23 andthe elastic force Fs of the miniature spring 245. The position of theslide sleeve 26 is adjusted to fine-tune the compression displacement ΔXof the miniature spring 245 to change the elastic force Fs. Adjustingthe position of the slide sleeve 26 is equivalent to adjusting themagnitude of the compression displacement ΔX and the magnitude of theelastic force Fs. Therefore, when the value of the elastic coefficient Kof the miniature spring 245 is fixed and the outer diameter d1 andweight W of the floating ball are also fixed, the elastic force Fs canbe changed to adjust the length of the shielding time Δt.

In the first and second embodiments, when the direction in which thefloating ball 23 bears the weight W is consistent with the direction ofthe pressing force Fp, the floating ball 23 will not deviate from theouter gas hole 227 and cannot discharge the residual gas quickly. Thereleasing mechanism 24 b/24 c/24 d of the third embodiment, the fourthembodiment or the fifth embodiment described later can solve such arestriction, that is, when the direction in which the floating ball 23bears the weight W is consistent with the direction of the pressingforce Fp, the floating ball 23 will not deviate from the outer gas hole227 and cannot discharge the residual gas quickly. The weight W of thefloating ball, the elastic force Fs, the magnetic force Fm and thepressing force Fp of the releasing mechanism have no directionrestrictions. In the third embodiment, the retaining nut set 244 can betightly locked on the retaining ring 25 a, and a pre-compression isapplied to the miniature spring 245, so that the adjusting shaft 240 isin a stable state and is not affected by the high-speed filling gas. Inthe fourth embodiment, the retaining nut set 244 can be tightly lockedon the adjusting disc 262 of the slide sleeve 26, and a pre-compressionis applied to the miniature spring 245, so that the adjusting shaft 240is in a stable state and is not affected by the high-speed filling gas.The pre-compression can be used to adjust the elastic force Fs of theminiature spring 245.

Fifth Embodiment

Please refer to FIG. 8A. The buffer valve 2 e is an independent device.The buffer valve 2 e includes a miniature valve body 21 e, a breathingcover 20 b, and a floating ball 23 a. The miniature valve body 21 e hasa cylindrical shape, and includes the inner chamber 222, an outerchamber 212, a partition portion 213, the outer gas hole 227, and amagnetic member 219. The outer chamber 212 is configured to mount thegas connector 16. The long cylindrical inner chamber 222 has the axis223, the inner annular surface 224, the inner end 225 and the outer end226. The breathing cover 20 b is configured to connect the breathinghole 141, and includes an inner micro gas hole 221, an inneraccommodating chamber 202, an external thread 203, and a central post204. The external thread 203 of the breathing cover 20 b is coupled andsealed with the breathing hole 141. The outer ring surface of theminiature valve body 2 e is coupled and sealed with the inneraccommodating chamber 202 of the breathing cover 20 b. The inner microgas hole 221 is deviated from the axis 223 of the inner accommodatingchamber 202 and is located at the inner end 225 close to the innerannular surface 224 to communicate with the breathing hole 141. Thecentral post 204 of the breathing cover 20 b is mounted at the center ofthe bottom of the inner accommodating chamber 202 and is concentric withthe axis 223 to extend in the inner chamber 222. The floating ball 23 ahas a cylindrical shape, and includes a spherical curved surface 232 atits front end and a cylinder 233 at its rear end. The cylinder 233 has acylindrical blind hole 234. A magnetic ring 235 is installed inside thefloating ball 23 a. The magnetic ring 235 is a long ring and isinstalled near the spherical curved surface 232. The axis 223 extends topass through the center of the spherical curved surface 232 and thecenter of the magnetic ring 235 and is concentric with the blind hole234. The partition portion 213 is located in the middle of the miniaturevalve body 21 e to separate the inner chamber 222 and the outer chamber212 at two ends. The outer gas hole 227 is disposed on the partitionportion 213 and located on the axis 223 to communicate with the innerchamber 222 and the outer chamber 212. The magnetic member 219 isannular and is mounted on the side of the partition portion 213 close tothe inner chamber 222 and is concentric with the outer gas hole 227. Thefloating ball 23 a is housed in the inner chamber 222 and can move backand forth on the central post 204. A mutually repulsive magnetic forceFm is generated between the magnetic ring 235 of the floating ball 23 aand the magnetic member 219 of the miniature valve body 21 e. Thefloating ball 23 a moves along with the gas flow in the inner chamber222. The outer diameter d1 of the floating ball 23 is less than theinner diameter D2 of the inner chamber 222, d1<D2.

In the high filling action 236, when the pneumatic chamber 14 is filledwith high-pressure gas, the gas flow 142 of the high-pressure gas willenter the inner flow channel 22 through the outer gas hole 227 from thehigh-pressure pipeline 161, and push the floating ball 23 a to the innerend 225 of the inner chamber 222 without covering the inner micro gashole 221, keeping the high-pressure gas entering the pneumatic chamberthrough the inner micro gas hole 221 to have the high filling action236.

When the high-pressure gas is released, the floating ball 23 a canperform the shielding action 230 on the outer gas hole 227. Theshielding action 230 is that when the high-pressure gas is released fromthe pneumatic chamber 14, the floating ball 23 will be attached to theouter gas hole 227. When the floating ball 23 completes the shieldingaction 230, a circular contact line C is formed between the floatingball and the entrance of the outer gas hole 227.

The shielding action 230 is that when the magnetic force Fm mutuallyrepelling the magnetic ring 235 of the floating ball 23 a and themagnetic member 219 of the miniature valve body 21 e cannot resist thepressing force Fp generated by the pressure difference ΔP, Fm<Fp, thefloating ball 23 a is secured to the outer gas hole 227.

When the outer diameter d1 of the floating ball 23 a is greater than theinner diameter d3 of the outer gas hole, the cone angle 2θ is definedbetween the circular contact line C generated by the shielding action230 and the center of the floating ball 23, 15°≤θ≤80°.

When the outer diameter d1 of the floating ball 23 is less than theinner diameter d3 of the outer gas hole 227, the annular area of the gapbetween the outer diameter d1 and the inner diameter d3 is not greaterthan 50% of the cross-sectional area of the inner micro gas hole 221 toachieve slow degassing (not shown).

When the pressure of the high-pressure gas decreases, the repulsivemagnetic force Fm that the floating ball 23 a bears overcomes thepressing force Fp to complete the releasing action 231. The releasingmechanism is that when the pressing force Fp generated by the pressuredifference ΔP cannot resist the magnetic force Fm of the magnetic ringand the magnetic member, Fm>Fp, the floating ball is displaced backwardto the inner chamber and no longer covers the outer gas hole.

The releasing mechanism 24 d is not restricted by the direction of theweight W of the floating ball and the direction of the pressing forceFp.

The releasing action 231 can be reliably completed due to the ratio ofthe outer diameter d1 of the floating ball 23 a to the inner diameter D2of the inner chamber 222, d1/D2≤0.8.

In the adjusting mechanism 28, the shielding time Δt can be determinedby the weight W and the outer diameter d1 of the floating ball 23 andthe mutually repulsive magnetic force Fm. The adjusting mechanism 28 ofthe magnetic force Fm refers to adjusting the mutual repulsive forcebetween the magnetic ring 235 and the magnetic member 219 of theminiature valve body.

The above embodiments all solve problem 1, problem 2, problem 3, problem4 and problem 5, and also fully meet requirement 1, requirement 2,requirement 3 and requirement 4, and meet the unique requirements fordelivering clean fluid and particle suspension fluid.

What is claimed is:
 1. A buffer valve, being a two-way valve, the buffer valve being installed on a pneumatic diaphragm valve, the pneumatic diaphragm valve including a pneumatic cylinder, a diaphragm and a valve seat, the pneumatic cylinder being divided into a pneumatic chamber and a spring chamber by a piston, a spring being disposed in the spring chamber, the pneumatic chamber and the spring chamber each having a breathing hole, the breathing hole of the pneumatic chamber having an inner accommodating chamber, the buffer valve being mounted to the inner accommodating chamber, the buffer valve being provided with a gas connector for filling a high-pressure gas, the buffer valve being configured to adjust a flow rate of the breathing hole, the buffer valve being used for adjusting release of the high-pressure gas in the pneumatic chamber without affecting a filling speed of the high-pressure gas in the pneumatic chamber, a tool part being disposed on an outside of the buffer valve for mounting or demounting the buffer valve and for mounting the gas connector; the diaphragm being an integral structure and having a circumferential portion, a central portion and an elastic portion, the elastic portion having a Ω-shaped cross section with an arc-shaped curve; characterized in that: in the process from an open state to a closed state for a normally closed valve and in the process from the closed state to the open state for a normally open valve, when the high-pressure gas is released, the buffer valve can slow down a pressure shock wave generated by the release of the high-pressure gas within a period of time, and the compressed spring in the spring chamber is restricted to slowly release its elastic force during expansion; an approach speed of the central portion of the diaphragm of the normally closed valve toward the valve seat is reduced to reduce impact and to reduce intense jet flow generated by the valve seat when it is closed; an instantaneous leaving speed of the central portion of the diaphragm of the normally open valve away from the valve seat is reduced to slow down generation of local negative pressure and reduce generation of intense eddy flow and intense turbulent flow; an inner flow channel of the buffer valve includes an inner micro gas hole, an inner chamber, an outer gas hole, and a floating ball; the inner flow channel is selectively in communication with the internal pneumatic chamber or the gas connector of an external high-pressure gas source; the inner chamber has an axis, an inner annular surface, an inner end and an outer end, the inner end communicates with the pneumatic chamber through the inner micro gas hole, the inner micro gas hole is disposed at a position deviating from the axis of the inner chamber and close to the inner annular surface, the outer end of the inner chamber communicates with the gas connector through the outer gas hole, the outer end of the inner chamber has a micro gas hole communicating with the gas connector, the cross-sectional area of the micro gas hole is not greater than 50% of the cross-sectional area of the inner micro gas hole, so as to achieve slow degassing, the outer gas hole is located on the axis of the inner chamber, and the floating ball is disposed in the inner chamber and floats along with the high-pressure gas, the floating ball having an outer diameter d1 less than an inner diameter D2 of the inner chamber, d1<D2; the buffer valve has the following functions in operation, including a high-filling action, a shielding action, a releasing action (including a releasing mechanism), a shielding time Δt, and an adjusting mechanism; the high-filling action is that when the pneumatic chamber is filled with the high-pressure gas, the high-pressure gas enters the inner chamber through the outer gas hole from a high-pressure pipeline and pushes the floating ball to move toward the inner micro gas hole, without covering the inner micro gas hole, allowing the high-pressure gas to enter the pneumatic chamber to have the high-filling action; the shielding action is that when the high-pressure gas is released from the pneumatic chamber, the high-pressure gas passes through the inner micro gas hole to enter the inner chamber and drives the floating ball to move toward the outer gas hole to cover the outer gas hole to slow down the release of high-pressure gas; the shielding action is caused by an opening of the floating ball and an inner diameter d3 of the outer gas hole to form a circular contact line C, the circular contact line C cannot achieve an airtightness effect but reduces the speed of gas leakage; the shielding action is caused by a pressure difference ΔP between a gas pressure and a pipeline pressure to generate a pressing force Fp on the floating ball, the pressing force Fp is equal to the pressure difference ΔP multiplied by a circular area of the circular contact line C; the releasing action is that when the high-pressure gas is continuously released under the shielding action, after the gas pressure is reduced, the releasing action is to release the pressing force Fp through the releasing mechanism, so that the floating ball is displaced and no longer covers the outer gas hole, and the residual high-pressure gas is discharged quickly; the releasing mechanism is a mechanism using at least one of a weight W of the floating ball, an elastic force Fs and a magnetic force Fm to resist the pressing force Fp and move the floating ball to complete the releasing action; the shielding time Δt is a period from the generation of the shielding action to the completion of the releasing action; the adjusting mechanism is that the length of the shielding time Δt is adjusted through the releasing mechanism of the releasing action.
 2. The buffer valve as claimed in claim 1, wherein a center of the floating ball is connected to the circular contact line to form a cone angle 2θ.
 3. The buffer valve as claimed in claim 1, wherein the circular contact line is a narrow annular band structure.
 4. The buffer valve as claimed in claim 1, wherein when the outer diameter d1 of the floating ball is less than the inner diameter d3 of the outer gas hole, d1<d3, the area of the circular contact line C is equal to the cross-sectional area of the outer diameter of the floating ball, the annular area of a gap between the outer diameter d1 and the inner diameter d3 is not greater than 50% of the cross-sectional area of the inner micro gas hole to achieve slow degassing.
 5. The buffer valve as claimed in claim 1, wherein the length of the shielding time Δt of the shielding action is proportional to the pressing force Fp; the length of the shielding time Δt of the shielding action is proportional to the size of the cone angle 2θ.
 6. The buffer valve as claimed in claim 1, wherein when the releasing mechanism uses the weight W of the floating ball, the shielding action is that when the weight W of the floating ball cannot resist the pressing force Fp, the floating ball is secured to the outer gas hole, and the releasing mechanism is that when the pressing force Fp generated by the pressure difference ΔP cannot resist the weight W of the floating ball, the floating ball is displaced to the inner chamber and no longer covers the outer gas hole.
 7. The buffer valve as claimed in claim 1, wherein when the releasing mechanism uses the elastic force Fs, the shielding action is that when the elastic force Fs borne by the floating ball cannot resist the pressing force Fp, the floating ball is secured to the outer gas hole, and the releasing mechanism is that when the pressing force Fp generated by the pressure difference ΔP cannot resist the elastic force Fs borne by the floating ball, the floating ball is displaced to the inner chamber and no longer covers the outer gas hole.
 8. The buffer valve as claimed in claim 1, wherein when the releasing mechanism uses the magnetic force Fm, the shielding action is that when the magnetic force Fm borne by the floating ball cannot resist the pressing force Fp, the floating ball is secured to the outer gas hole, and the releasing mechanism is that when the pressing force Fp generated by the pressure difference ΔP cannot resist the magnetic force Fm borne by the floating ball, the floating ball is displaced to the inner chamber and no longer covers the outer gas hole.
 9. The buffer valve as claimed in claim 1, wherein the buffer valve includes a miniature valve body, the breathing hole and the floating ball; the miniature valve body has a cylindrical shape and includes the inner chamber, an outer chamber, a partition portion, and the outer gas hole; the breathing hole includes an inner accommodating chamber and the inner micro gas hole, the breathing hole is disposed on an outer ring wall of the pneumatic chamber, the inner micro gas hole is disposed at a position where the inner accommodating chamber deviates from the axis of the inner chamber and is close to the inner annular surface, an outer ring surface of the miniature valve body is coupled and sealed with the inner accommodating chamber of the breathing hole; the outer chamber is configured to install the gas connector; the partition portion is located in the middle of the miniature valve body to separate the inner chamber and the outer chamber at two ends, the partition portion has the outer gas hole to communicate with the inner chamber and the outer chamber, and the outer gas hole is located on the axis; the shielding action is that when the weight W of the floating ball cannot resist the pressing force Fp, the floating ball is secured to the outer gas hole; the releasing mechanism is that when the weight W of the floating ball exceeds the pressing force Fp generated by the pressure difference ΔP, the floating ball is displaced to the inner chamber and no longer covers the outer gas hole; the releasing action is reliably completed due to the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner chamber, d1/D2≤0.6; the outer diameter d1 of the floating ball is greater than the outer diameter d3 of the outer gas hole, and the cone angle 2θ, 10°≤θ≤60°; wherein the adjusting mechanism is configured to adjust parameters including the weight W and the outer diameter d1 of the floating ball and the cone angle 2θ.
 10. The buffer valve as claimed in claim 1, wherein the buffer valve includes a miniature valve body, a breathing cover and the floating ball; the miniature valve body has a cylindrical shape and includes the inner chamber, an outer chamber, a partition portion, and the outer gas hole; the breathing cover is configured to connect the breathing hole and includes an inner accommodating chamber, the inner micro gas hole, and an external thread; an external thread of the breathing cover is coupled and sealed with the breathing hole; the inner micro gas hole is located on the breathing cover at a position where the inner accommodating chamber deviates from the axis of the inner chamber and is close to the inner annular surface to communicate with the breathing hole; an outer ring surface of the miniature valve body is coupled and sealed with the inner accommodating chamber of the breathing cover; the outer chamber is configured to install the gas connector; the partition portion is located in the middle of the miniature valve body to separate the inner chamber and the outer chamber at two ends, the partition portion has the outer gas hole to communicate with the inner chamber and the outer chamber, and the outer gas hole is located on the axis; the shielding action is that when the weight W of the floating ball cannot resist the pressing force Fp, the floating ball is secured to the outer gas hole; the releasing mechanism is that when the weight W of the floating ball exceeds the pressing force Fp generated by the pressure difference ΔP, the floating ball is displaced to the inner chamber and no longer covers the outer gas hole; the releasing action is reliably completed due to the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner chamber, d1/D2≤0.6; the outer diameter d1 of the floating ball is greater than the outer diameter d3 of the outer gas hole, and the cone angle 2θ, 10°≤θ≤60°; wherein the adjusting mechanism is configured to adjust parameters including the weight W and the outer diameter d1 of the floating ball and the cone angle 2θ.
 11. The buffer valve as claimed in claim 1, wherein the buffer valve includes a miniature valve body, the breathing hole, the floating ball, a releasing mechanism, a retaining ring, and an adapter; the miniature valve body has a cylindrical shape and includes the inner chamber, a connecting chamber, a partition portion, and the outer gas hole; the breathing hole includes the inner accommodating chamber and the inner micro gas hole, the breathing hole is disposed on an outer ring wall of the pneumatic chamber; an outer ring surface of the miniature valve body is coupled and sealed with the inner accommodating chamber of the breathing hole; the inner micro gas hole is disposed at a position where the inner accommodating chamber deviates from the axis of the inner chamber and is close to the inner annular surface; the partition portion is disposed between the inner chamber and the connecting chamber, the partition portion has the outer gas hole to communicate with the connecting chamber and the inner chamber, the outer gas hole is located on the axis; an inner diameter of the connecting chamber is greater than that of the inner chamber, the retaining ring and the adapter are secured in an airtightness manner; the adapter is installed at an open end of the connecting chamber and is located outside the retaining ring, the adapter is configured to connect the gas connector and the high-pressure pipeline and communicates with the pneumatic chamber; the retaining ring has a cylindrical shape and includes a shaft hole and at least one ventilation hole, the retaining ring is secured to a bottom of the connecting chamber and pressed against the partition portion, the shaft hole has an inner diameter less than that of the outer gas hole, the ventilation hole is in communication with the outer gas hole; the releasing mechanism includes an adjusting shaft, the retaining ring, a retaining nut set, and a miniature spring; the adjusting shaft includes an external thread, a ball seat and a shaft, the disc-shaped ball seat is located at one end of the adjusting shaft and has a concave spherical surface, the external thread is located at another end of the adjusting shaft; in assembly, the retaining ring is firstly locked inside the connecting chamber, the adjusting shaft is inserted in the miniature spring with its tail end passing through the outer gas hole and the shaft hole from the side of the inner chamber, so that the external thread is located in the connecting chamber to keep the ball seat at the side of the inner chamber, the miniature spring is sleeved on the shaft and pressed between the ball seat and the retaining ring; the inner diameter of the outer gas hole is greater than an outer diameter of the ball seat, so that the adjusting shaft can move back and forth in the inner chamber and the outer gas hole freely; the shaft is in sliding fit with the shaft hole to support the adjusting shaft; the external thread of the adjusting shaft extends out of the shaft hole, the retaining nut set is disposed on the external thread to ensure that the adjusting shaft will not be loosened from the retaining ring when the high-pressure gas is filled; the shielding action is that when the high-pressure gas brings the floating ball to be attached to the ball seat, a pressing force Fp generated by the pressure difference ΔP generated by the high-pressure gas is applied to the floating ball, the miniature spring is pushed back by the ball seat to generate a compression displacement ΔX and the elastic force Fs, the compression displacement ΔX is the compression amount of the miniature spring, Fp≥Fs; the releasing action is that when the pressing force Fp generated by the pressure difference ΔP cannot resist the elastic force Fs of the miniature spring, Fp≤Fs, the floating ball is pushed away and moved to the inner chamber without covering the outer gas hole; the releasing mechanism is not restricted by the direction of the weight W of the floating ball and the direction of the pressing force Fp; the releasing mechanism is reliably completed due to the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner chamber, d1/D2≤0.8; the outer diameter d1 of the floating ball is greater than the inner diameter d3 of the outer gas hole, the cone angle 2θ, 15°≤θ≤80°; the adjusting mechanism, the shielding time Δt is adjusted by the weight W and the outer diameter d1 of the floating ball and the elastic force Fs of the miniature spring, and the adjustment of the elastic force Fs refers to adjusting the elastic coefficient of the miniature spring; the adjusting mechanism includes the retaining nut set, the relative position of the ball seat of the adjusting shaft relative to an opening of the outer gas hole at the side of the inner chamber can be set to ensure that the floating ball can indeed complete the shielding action and the releasing action.
 12. The buffer valve as claimed in claim 1, wherein the buffer valve includes a miniature valve body, the breathing hole, the floating ball, a releasing mechanism, a retaining ring, a slide sleeve, and an adapter; the miniature valve body has a cylindrical shape and includes the inner chamber, a connecting chamber, a partition portion, and the outer gas hole; the breathing hole includes an inner accommodating chamber and the inner micro gas hole, the breathing hole is disposed on an outer ring wall of the pneumatic chamber; an outer ring surface of the miniature valve body is coupled and sealed with the inner accommodating chamber of the breathing hole; the inner micro gas hole is disposed at a position where the inner accommodating chamber deviates from the axis of the inner chamber and is close to the inner annular surface; the partition portion is disposed between the inner chamber and the connecting chamber, the partition portion has the outer gas hole to communicate with the outer chamber and the connecting chamber, the outer gas hole is located on the axis; an inner diameter of the connecting chamber is greater than that of the inner chamber, the retaining ring and the adapter are secured in an airtightness manner; the adapter is installed at an open end of the connecting chamber and is located outside the retaining ring, the adapter is configured to connect the gas connector and the high-pressure pipeline and communicates with the pneumatic chamber; the retaining ring has a cylindrical shape and includes at least one ventilation hole and a central screw hole, the retaining ring is secured to a bottom of the connecting chamber and pressed against the partition portion, the central screw hole has an inner diameter less than that of the outer gas hole, the ventilation hole is in communication with the outer gas hole; the releasing mechanism has an adjusting shaft, the slide sleeve, the retaining ring, a locking nut, the retaining nut set, and a miniature spring; the adjusting shaft includes an external thread, a ball seat and a shaft, the disc-shaped ball seat is located at one end of the adjusting shaft and has a concave spherical surface, the external thread is located at another end of the adjusting shaft; the slide sleeve includes a slide shaft hole, an adjusting disc, and an external thread; in assembly, the retaining ring is firstly locked inside the connecting chamber, the locking nut is fitted on the external thread of the slide sleeve and screwed to the position of the adjusting disc, the external thread of the slide sleeve is coupled with the central screw hole of the retaining ring, the adjusting shaft is inserted in the miniature spring with its tail end to passthrough the outer gas hole and the slide shaft hole from the side of the inner chamber, so that the external thread is located in the connecting chamber to keep the ball seat at the side of the inner chamber, an outer diameter of the external thread of the slide sleeve is greater than an outer diameter of the miniature spring, the miniature spring is sleeved on the shaft and pressed between the ball seat and the slide sleeve; the inner diameter of the outer gas hole is greater than an outer diameter of the ball seat, so that the adjusting shaft can move back and forth in the inner chamber and the outer gas hole freely; the shaft is in sliding fit with the slide shaft hole to support the adjusting shaft; the adjusting disc of the slide sleeve is rotated to move forward or rearward and is secured by the locking nut, the position of the miniature spring is linked with the position of the slide sleeve to change a compression displacement ΔX; the external thread of the adjusting shaft extends out of the slide shaft hole of the slide sleeve, the retaining nut set is disposed on the external thread to ensure that the adjusting shaft will not be loosened from the slide sleeve when the high-pressure gas is filled; the position of the slide sleeve is adjusted to fine-tune the compression displacement ΔX of the miniature spring to change the elastic force Fs, when the value of the elastic coefficient K of the miniature spring is fixed and the outer diameter d1 and weight W of the floating ball are also fixed, the elastic force Fs can be changed to adjust the length of the shielding time Δt; the shielding action is that when the high-pressure gas brings the floating ball to be attached to the ball seat, a pressing force Fp generated by the pressure difference ΔP generated by the high-pressure gas is applied to the floating ball, the miniature spring is pushed back by the ball seat to generate a compression displacement ΔX and the elastic force Fs, the compression displacement ΔX is the compression amount of the miniature spring, Fp≥Fs; the releasing action is that when the pressing force Fp generated by the pressure difference ΔP cannot resist the elastic force Fs of the miniature spring, Fp≤Fs, the floating ball is pushed away and moved to the inner chamber without covering the outer gas hole; the releasing mechanism is not restricted by the direction of the weight W of the floating ball and the direction of the pressing force Fp; the releasing mechanism is reliably completed due to the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner chamber, d1/D20.8; the outer diameter d1 of the floating ball is greater than the inner diameter d3 of the outer gas hole, the cone angle 2θ, 15°≤θ≤80°; the adjusting mechanism, the shielding time Δt is adjusted by the weight W and the outer diameter d1 of the floating ball and the elastic force Fs of the miniature spring, and the adjustment of the elastic force Fs refers to adjusting the elastic coefficient of the miniature spring; the adjusting mechanism includes the retaining nut set, the relative position of the ball seat of the adjusting shaft relative to an opening of the outer gas hole at the side of the inner chamber can be set to ensure that the floating ball can indeed complete the shielding action and the releasing action.
 13. The buffer valve as claimed in claim 1, wherein the buffer valve includes a miniature valve body, a breathing cover and a floating ball; the miniature valve body has a cylindrical shape and includes the inner chamber, an outer chamber, a partition portion, the outer gas hole, and a magnetic member; the outer chamber is configured to mount the gas connector; the breathing cover is configured to connect the breathing hole and includes an inner accommodating chamber, the inner micro gas hole, an external thread, and a central post; the external thread of the breathing cover is coupled and sealed with the breathing hole; an outer ring surface of the miniature valve body is coupled and sealed with the inner accommodating chamber of the breathing cover; the central post of the breathing cover is mounted at a central position of a bottom of the inner accommodating chamber and is concentric with the axis to extend in the inner chamber; the inner micro gas hole is deviated from the axis of the inner accommodating chamber and is located at the inner end close to the inner annular surface to communicate with the breathing hole; the floating ball has a cylindrical shape and includes a spherical curved surface at its front end and a cylinder at its rear end, the cylinder has a cylindrical blind hole, a magnetic ring is installed inside the floating ball, the magnetic ring is a long ring located near the spherical curved surface, the axis extends to pass through the center of the spherical curved surface and the center of the magnetic ring and is concentric with the blind hole; the partition portion is located in the middle of the miniature valve body to separate the inner chamber and the outer chamber at two ends, the inner chamber and the outer chamber are in communication with each other through the outer gas hole, the outer gas hole is located on the axis; the magnetic member is annular and is mounted on one side of the partition portion close to the inner chamber and is concentric with the outer gas hole; the floating ball is disposed in the inner chamber and can move back and forth on the central post; a mutually repulsive magnetic force Fm is generated between the magnetic ring of the floating ball and the magnetic member of the miniature valve body; the shielding action is that when the magnetic force Fm mutually repelling the magnetic ring of the floating ball and the magnetic member of the miniature valve body cannot resist the pressing force Fp generated by the pressure difference ΔP, Fm<Fp, the floating ball is secured to the outer gas hole; the releasing mechanism is that when the pressing force Fp generated by the pressure difference ΔP cannot resist the magnetic force Fm mutually repelling the magnetic ring and the magnetic member, Fm>Fp, the floating ball is displaced backward to the inner chamber and no longer covers the outer gas hole.
 14. The buffer valve as claimed in claim 13, wherein the releasing mechanism is not restricted by the direction of the weight W of the floating ball and the direction of the pressing force Fp.
 15. The buffer valve as claimed in claim 13, wherein the releasing action is reliably completed due to the ratio of the outer diameter d1 of the floating ball to the inner diameter D2 of the inner chamber, d1/D2≤0.9.
 16. The buffer valve as claimed in claim 13, wherein when the outer diameter d1 of the floating ball is greater than the inner diameter d3 of the outer gas hole, the cone angle 2θ, 10°≤θ≤80°.
 17. The buffer valve as claimed in claim 13, wherein in the adjusting mechanism, the shielding time Δt is adjusted by the outer diameter d1 and the magnetic force Fm, the adjusting mechanism of the magnetic force Fm refers to adjusting a mutual repulsive force between the magnetic ring and the magnetic member of the miniature valve.
 18. The buffer valve as claimed in claim 1, wherein the weight W of the floating ball, the elastic force Fs, the magnetic force Fm and the pressing force Fp of the releasing mechanism have no direction restrictions.
 19. The buffer valve as claimed in claim 1, wherein in the process from the open state to the closed state for the normally closed valve and in the process from the closed state to the open state for the normally open valve, when the high-pressure gas is released, the buffer valve is actuated immediately, the approach speed of the central portion of the diaphragm the normally closed valve to the valve seat is reduced immediately, and the leaving speed of the central portion of the diaphragm of the normally open valve from the valve seat is reduced immediately.
 20. The buffer valve as claimed in claim 19, wherein in the process from the open state to the closed state for the normally closed valve and in the process from the closed state to the open state for the normally open valve, the period of time is that when the high-pressure gas is released, the shielding time Δt of the buffer valve is to slow down the pressure shock wave generated by the release of the high-pressure gas in the whole process; the approach speed of the central portion of the diaphragm of the normally closed valve toward the valve seat is reduced in the whole process to reduce impact and to reduce intense jet flow generated by the valve seat when it is closed; the leaving speed of the central portion of the diaphragm of the normally open valve away from the valve seat is reduced in the whole process to slow down generation of local negative pressure and reduce generation of intense eddy flow and intense turbulent flow. 